Stepless speed change transmission device pressurized by movable cone disc

Abstract

The invention belongs to the technical field of transmissions, and relates to a stepless speed change transmission device pressurized by a movable conical disc, which comprises a first-shaft conical disc unit, a second-shaft conical disc unit, an annular transmission part used for being in transmission connection with the first-shaft conical disc unit and the second-shaft conical disc unit, a thrust unit and a torsion unit, the thrust unit comprises a main thrust disc arranged at the non-conical-surface end of a first shaft moving conical disc, and the main thrust disc is connected with a first shaft in a circumferential fixing and axial moving mode. Torque is transmitted between the main thrust disc and the first shaft moving cone disc, axial thrust can be generated on the first shaft moving cone disc, and meanwhile clamping force needed by torque transmission of the annular transmission piece is formed. The axial stroke generated by mutual rotation between the main thrust disc and the first shaft moving cone disc is matched with the axial stroke needed by speed regulation of the first shaft moving cone disc. The torsion unit comprises a main torsion disc which is arranged on the first shaft in a sleeving mode in an axial sliding and circumferential fixing mode, and the main torsion disc is used for providing forward rotation torque for the power source.

Description

Technical Field

[0001] The invention belongs to the technical field of transmissions, and relates to a continuously variable transmission device with a dynamic cone disc pressurized. Background Art

[0002] The continuously variable transmission device transmits power by establishing rolling friction through the conical surfaces of two pairs of cone disks to clamp the annular transmission parts (metal belts, rubber belts, etc.); speed regulation is achieved by changing the rolling radius of the annular transmission parts on the cone disks; when the annular transmission parts transmit the same torque at different working radii, the required clamping force is negatively correlated with the working radius; the technical upgrades and progress of the continuously variable transmission device mainly focus on breakthroughs in its pressurized clamping force system and speed regulation system (referred to as speed regulation).

[0003] The common continuously variable transmission devices today use hydraulic systems to establish thrust to provide clamping force and speed regulating force to the moving cone disc. The disadvantages are: 1. Power transmission lag ("meat"); 2. Excessive clamping force needs to be established to reduce impact damage, resulting in reduced life, reliability and mechanical transmission efficiency; 3. The hydraulic system manufacturing process and control system are complex and costly; 4. The speed regulating thrust is required to be large, resulting in high costs for the hydraulic pump and its control system. The above performance disadvantages and cost factors limit the application of this solution in a wider range of fields (such as heavy-duty trucks, medium and large agricultural tractors, some wind turbines, etc.).

[0004] In order to solve the problems of the above-mentioned hydraulic solution, the existing technology attempts to provide the clamping force required for transmitting power through a slope pressure structure, that is, the two slope rollers generate clamping force through the rolling and twisting of the clamped steel balls; its advantage is that the slope pressure structure can provide the required clamping force in real time during the power transmission process, avoiding the shortcomings of the hydraulic system in providing clamping force.

[0005] Practice has found that the existing slope pressure structure has the following problems: 1. The slope pressure structure is set on the side of the dynamic cone, and it is impossible to transmit torque in the reverse direction. For example, the electric vehicle cannot be pressurized during the switching process from the reverse dragging condition to the braking energy recovery condition; 2. The slope pressure structure has mechanical clearance due to the wear of the annular transmission parts, inelastic elongation and assembly, which causes oscillation shock when transmitting power (test data is attached). Fig.14 3. The slope pressure structure is set on the fixed cone side, and there is excess clamping force, resulting in low mechanical transmission efficiency; 4. The slope pressure structure is set on the fixed cone side, and the active speed regulation system has poor adaptability (high cost and component performance cannot meet the use requirements).

[0006] Patent document No. DE000010139119 discloses a technical solution for providing clamping force to the movable cone disc through a slope pressure structure, but still fails to solve the above-mentioned problems of impact and reverse power transmission; Patent document No. CN117386773A discloses a technical solution for providing clamping force to the fixed cone disc through a slope pressure structure, and the speed reduction motor system and its actuator drive the movable cone discs of the driving shaft and the driven shaft to move axially in the same direction synchronously for speed regulation; but there are the following disadvantages: 1. This solution attempts to reduce the impact (angular impulse) by changing the transmission path of the preload elastic component, but its key idea is still to eliminate the mechanical clearance by extending the preload elastic component to push the slope pressure structure and the cone disc to move axially, and compress the preload elastic component during the transmission of power. 1. The components will still bring about vibration and impact problems; 2. The slope pressure structure is set on the fixed cone side, and the slope raceway angles corresponding to different transmission speed ratios cannot be reasonably adapted, resulting in excessive clamping force, which reduces the mechanical transmission efficiency and service life; 3. The electromechanical speed control system leads to increased costs, complex structure and reduced reliability; 4. The electromechanical speed control system needs to be equipped with 4 bearings that withstand high speed and high thrust to isolate the speed of the speed control system, which reduces the mechanical transmission efficiency; 5. The cone-disk continuously variable transmission used in medium and large vehicle machinery (such as power source torque of more than 400Nm) has a maximum speed control thrust of more than 10 tons and withstands a speed of more than 8000rpm. The physical limit of the thrust bearing cannot effectively adapt to the requirements of such working conditions, which limits the application and promotion of this solution.

[0007] In order to simplify the speed regulation structure and reduce the system cost, the patent document with the publication number CN114838098A discloses a method of arranging the slope pressure structure and the active pressure elastic component in series on the side of the dynamic cone disk of the driving shaft to provide the clamping force and the axial displacement required for speed regulation, and the driven shaft is provided with a reduction motor system and its actuator to drive the driven shaft dynamic cone disk for active speed regulation; the disadvantages of this scheme are as follows: 1. The slope pressure structure will still produce impact in the process of transmitting power to compress the active pressure elastic component and transmitting power in the forward and reverse directions, which reduces the service life and reliability; 2. When transmitting small and medium torques, the active pressure elastic component has the problem of excessive clamping force resulting in low mechanical efficiency; 3. The scheme is still provided with an electromechanical system for active speed regulation, and the possibility of further cost reduction is not achieved; 4. The electromechanical speed regulation system still needs to be provided with a bearing that can withstand large thrust and high speed, which reduces the mechanical transmission efficiency. At the same time, the poor adaptability of the thrust bearing limits the application field of this scheme. Summary of the invention

[0008] In view of this, the main purpose of the present invention is to provide a continuously variable transmission device with dynamic cone disc pressurization to solve the problems that the existing slope pressurization structure is set on the dynamic cone disc side and cannot transmit power in the reverse direction, there is oscillation impact when transmitting power, and the active speed regulation system cannot be effectively adapted and the cost is high.

[0009] In order to achieve the above object, the present invention provides the following technical solutions:

[0010] A continuously variable transmission device with a dynamic cone disc pressurized, comprising a one-shaft cone disc unit, a two-shaft cone disc unit, and an annular transmission member for transmission connection between the one-shaft cone disc unit and the two-shaft cone disc unit, wherein the one-shaft cone disc unit comprises a shaft, a one-shaft fixed cone disc and a one-shaft dynamic cone disc; the one-shaft fixed cone disc is sleeved on the one shaft in a manner that it can rotate with each other and is fixed in at least one axial direction, and the one-shaft dynamic cone disc is sleeved on the one-shaft fixed cone disc in a manner that is fixed in the circumferential direction and slides in the axial direction; the two-shaft cone disc unit comprises two shafts and two-shaft fixed cone discs and two-shaft dynamic cone discs with cone surfaces arranged opposite to each other; the one shaft or the two shafts is 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 and a torque unit;

[0011] The thrust unit comprises a thrust rolling body and a main thrust disc arranged on the non-conical surface side of a shaft-moving cone disc, the main thrust disc is connected to a shaft in a circumferentially fixed and axially movable manner, the main thrust disc and the non-conical surface end of the shaft-moving cone disc are respectively provided with a main thrust ramp groove and a secondary thrust ramp groove which are centrally symmetrical with respect to clamping the thrust rolling body, so that when the main thrust disc and the shaft-moving cone disc transmit torque, an axial thrust can be generated on the shaft-moving cone disc, and the clamping force required for the annular transmission member to transmit torque is formed, and the axial stroke generated by the mutual rotation between the main thrust disc and the shaft-moving cone disc matches the axial stroke required for the speed regulation of the shaft-moving cone disc;

[0012] The torque unit comprises a main torque plate which is sleeved on the one shaft in an axially sliding and circumferentially fixed manner, and the main torque plate is used to provide a forward rotation torque to the power source.

[0013] Furthermore, the torsion unit further comprises a torsion rolling body and a shaft second elastic component;

[0014] The main torque disc is arranged on one side of the non-conical surface end of a shaft-moving cone disc, and a main torque ramp groove and a secondary torque ramp groove are respectively provided in the circumferential direction of the main torque disc and the non-conical surface end of the shaft-moving cone disc, which are symmetrically distributed around the center of the torsion rolling body. Both the main torque ramp groove and the secondary torque ramp groove are unidirectional ramp grooves that rise from one end to the other end, and at least two groups of secondary torque ramp grooves and main torque ramp grooves that are evenly distributed along the circumferential direction are provided;

[0015] One end of the second elastic component of the first shaft abuts against the end surface of the main torque disc on the side away from the main torque ramp groove and provides the main torque disc with axial pressure toward the auxiliary torque ramp groove.

[0016] Further, the thrust unit further comprises a first elastic component of an axis, the first elastic component of an axis is sleeved on an axis and arranged on a side of the main thrust disc away from the axis-moving cone disc, so as to provide an axial thrust to the main thrust disc in the direction of the axis-moving cone disc, and an end surface of the main thrust disc away from the axis-moving cone disc abuts against a fifth support seat fixedly connected to the axis;

[0017] At least two groups of auxiliary thrust ramp grooves and main thrust ramp grooves are evenly distributed along the circumferential direction of the main thrust disc, and the auxiliary thrust ramp grooves and main thrust ramp grooves are both V-shaped slope groove structures that rise symmetrically from a low point to both ends or unidirectional slope grooves that rise from one end to the other end.

[0018] 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 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 minimum working radius in the one shaft cone disk unit.

[0019] 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 a position close to the highest point in the main thrust ramp groove, the torsion rolling body is arranged at a 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.

[0020] Furthermore, it also includes a centrifugal speed regulating unit; the two-shaft fixed cone disc is fixedly connected to the two-shaft sleeve, and the two-shaft movable cone disc is connected to the two-shaft sleeve in a circumferentially fixed and axially movable manner;

[0021] The centrifugal speed regulation unit includes a dynamic centrifugal disc, a fixed centrifugal disc, a centrifugal block and a first elastic component of two shafts. The dynamic centrifugal disc is abutted against the dynamic cone discs of the two shafts, and the first elastic component of the two shafts is abutted against the dynamic centrifugal disc. The axially opposite end faces 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 centrifugal block is clamped between the dynamic centrifugal slope groove and the fixed centrifugal slope groove. Under the action of the rotating centrifugal force, the centrifugal block compresses the first elastic component of the two shafts and causes the dynamic centrifugal disc to move axially, while providing space for synchronous and unidirectional axial movement of the dynamic cone discs of the two shafts for speed regulation.

[0022] Furthermore, the dynamic centrifugal ramp groove and the fixed centrifugal ramp groove are radially inclined raceways extending from low to high, and at least two groups of dynamic centrifugal ramp grooves and fixed centrifugal ramp grooves are arranged evenly distributed along the circumferential direction to clamp the centrifugal body.

[0023] Furthermore, when the one shaft is connected to a power source and serves as a driving shaft, the fixed centrifugal disc is fixedly sleeved on the two shafts and arranged on one side of the non-conical surface end of the dynamic conical disc of the two shafts, and the dynamic centrifugal disc is sleeved on the two shafts in an axially movable and circumferentially fixed manner and arranged on a side of the fixed centrifugal disc away from the dynamic conical disc of the two shafts;

[0024] The fixed centrifugal disc is provided with a through hole, so that the non-conical end of the two-axis dynamic cone 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;

[0025] In the installed state, the annular transmission member is at the maximum working radius of the two-shaft cone disk unit, and in the process of transmitting torque, the axial thrust generated by the thrust unit acts on the two-shaft dynamic cone disk through the annular transmission member. The thrust is smaller than the elastic force of the first elastic component of the two shafts.

[0026] Furthermore, when the two shafts are connected to a power source and serve as driving shafts, the centrifugal speed regulating unit further includes a second elastic component of the two shafts;

[0027] One end of the second elastic component of the second shaft is fixedly connected to the second shaft sleeve, and the other end is pressed against the non-conical surface end of the movable cone disk of the second shaft, and provides a thrust to the movable cone disk of the second shaft toward the fixed cone disk of the second shaft. The second elastic component of the second 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 second shaft is smaller than the elastic coefficient of the first elastic component of the second shaft;

[0028] The dynamic centrifugal disk 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 fixed conical disk of the two shafts. The fixed centrifugal disk is fixedly connected with the non-conical surface end of the fixed conical disk of the two shafts or is integrally formed and manufactured, and is arranged on one side of the dynamic centrifugal disk close to the fixed conical disk of the two shafts;

[0029] The two-shaft fixed conical disc and the fixed centrifugal disc are both provided with through holes, and the dynamic centrifugal disc abuts against the two-shaft dynamic conical disc via a speed regulating push rod passing through the through holes;

[0030] In the installed state, the first elastic component of the second shaft compresses the second elastic component of the second shaft through the speed regulating push rod, and the annular transmission member is at the minimum working radius in the second shaft cone disk unit. In addition, in this state, the length of the speed regulating push rod is sufficient for the second shaft dynamic cone disk to not bear the elastic force of the first elastic component of the second shaft, so that the preload force of the annular transmission member only comes from the torque unit.

[0031] Furthermore, 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 body, and the diameters of the torsion rolling body and the centrifugal body satisfy the following relationship:

[0032]

[0033]

[0034] L1≥2*(R max -R min )*tan a1 / 0.9 / sin a2

[0035] L2≥(R max -R min )*tan a1 / 0.9 / sin a2

[0036] d≥(R max -R min )*tan a1*2 / 0.9

[0037] 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; L1 is the raceway length when the main thrust ramp groove and the secondary thrust ramp groove are V-shaped slope groove structures; L2 is the raceway length when the main thrust ramp groove and the secondary thrust ramp groove are unidirectional slope grooves that rise from one end to the other end; 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.

[0038] The beneficial effects of the present invention are:

[0039] 1. During the process of switching the torque transmitted by the power source between the positive and reverse directions (such as switching the electric vehicle from the driving condition to the braking energy recovery condition), the torque rolling element of the torque unit climbs and compresses the second elastic component of the first axis and provides the clamping force required for transmitting the torque during the switching process. At the same time, the first elastic component of the first axis pushes the main thrust plate to move axially and presses the thrust rolling element, ensuring that the thrust rolling element can roll in the reverse direction to the symmetrical position of the V-shaped thrust ramp groove during the process, thereby providing the thrust to meet the clamping force required for transmitting the reverse torque (braking energy recovery). This function is suitable for the condition where electric vehicles transmit large torque in the reverse direction during braking energy recovery;

[0040] 2. When the power source is in the reverse drag condition (e.g. the vehicle is sliding to drive the power source to rotate and the power source does not output reverse torque), the torque unit provides clamping force to the annular transmission member and keeps the main thrust plate and the one-axis dynamic cone plate from rotating relative to each other; that is, the torque unit can provide the clamping force required to transmit the reverse drag torque of the power source;

[0041] 3. Due to the inelastic elongation, normal wear and tear between the annular transmission member and the cone disk unit, and assembly, there is a mechanical gap between the annular transmission member and the cone disk unit. The existing technical solution eliminates the mechanical gap by providing an axial thrust through a preloaded elastic member. However, there will be oscillation impact in the process of transmitting power to compress the preloaded elastic member, resulting in the service life and smoothness not meeting the use requirements. The second elastic component of one shaft in the torque unit of the present invention pushes the main torque disk to squeeze the torsion rolling body to roll in the main torsion ramp groove and the auxiliary torsion ramp groove, which can provide a torque consistent with the direction of the power torque (the torque is greater than the reverse drag torque at the peak speed of the power source) to one shaft, and overcome the rotational resistance torque of the power source to drive the power source to rotate until the mechanical gap is eliminated. That is, in the installed state or before power is transmitted, the torque unit has eliminated the mechanical gap, avoiding oscillation impact in the power transmission process, and significantly improving the service life and practicability.

[0042] 4. By setting the torque unit, the thrust unit is set on the side of the moving cone disc, and the centrifugal force of the centrifugal speed regulating unit compresses the elastic member to provide the moving cone disc with displacement. The moving cone disc on the thrust unit side does not need to be set with a speed regulating structure to achieve adaptive speed regulation, which effectively simplifies the structure, reduces costs, and improves reliability; and there is no need to set a thrust bearing that can withstand large thrust and high speed, which improves the mechanical transmission efficiency and significantly broadens the scope of application of the technical solution;

[0043] 5. The magnitude of the torque generated by the torque unit is related to the angles of the main torque ramp groove, the auxiliary torque ramp groove and the elastic coefficient of the first elastic component. In practical applications, the adaptive design can be made according to the rotational resistance torque of the power source to automatically work without setting up a complex active control system, which effectively improves the reliability of the system; when adapting to the internal combustion engine power source, the clamping force required to transmit the anti-drag torque can be provided by the torque unit, that is, the main thrust ramp groove and the auxiliary thrust ramp groove can be set to be unidirectional;

[0044] 6. The centrifugal force of the centrifugal speed regulating unit does not directly drive the moving cone disc to adjust the speed, thus avoiding the excessive clamping force caused by the centrifugal force at high speed, improving the mechanical transmission efficiency and service life, and reducing the structural strength design requirements;

[0045] 7. Since the motor can output constant power in the range from rated speed to 2 times rated speed, and the peak power of the internal combustion engine usually occurs at the highest speed and increases monotonically, the thrust unit is arranged on the side of the moving cone disc, and the centrifugal speed regulating unit, thrust unit, and torque unit can be flexibly adapted according to the speed and power characteristics of the power source, thereby improving the scope of application of the present invention;

[0046] 8. The thrust unit is set on the side of the moving cone disc. The angles of the main thrust ramp groove and the secondary thrust ramp groove can be designed according to the corresponding transmission speed ratio, which avoids excessive clamping force caused by setting the thrust unit on the side of the fixed cone disc, resulting in low mechanical transmission efficiency and reduced service life;

[0047] It is worth emphasizing that the above beneficial effects are mainly due to the fact that the torque unit of the present invention solves the problems of the slope pressurization structure, that the dynamic cone disc pressurization cannot transmit power in the reverse direction and that the transmitted power has oscillation impact, which is a prerequisite for feasibility.

[0048] 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

[0049] 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:

[0050] Figure 1 It is a structural schematic diagram of a cone-disk type continuously variable transmission device with a dynamic cone disk pressurized in Example 1;

[0051] Figure 2 is a schematic structural diagram of the torsion unit in Example 3;

[0052] Figure 3 for Figure 2 Schematic diagram of the arrangement of the mid-circumferential elastic components;

[0053] Figure 4 It is a structural schematic diagram of the auxiliary thrust ramp groove and the main thrust ramp groove being set as a one-way ramp groove;

[0054] Figure 5 It is a structural schematic diagram of a cone-disk type continuously variable transmission device with a dynamic cone disk pressurized in Example 2;

[0055] Figure 6 for Figure 1 The right view of the movable cone disc, auxiliary thrust ramp groove and auxiliary torque ramp groove of the middle shaft;

[0056] Figure 7 for Figure 1 The right side view of the moving centrifugal disc in FIG.

[0057] Figure 8 A schematic diagram of a prior art solution and a mechanical gap generated therefrom;

[0058] Fig. 9 It is a schematic diagram of the position of thrust rolling when the mechanical clearance is eliminated by axial thrust in the prior art solution;

[0059] Fig.10 This is a schematic diagram of the position of the thrust rolling element when the existing technical solution transmits power and causes impact;

[0060] Fig.11 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 1, where the torsion unit eliminates the mechanical clearance by driving the power source to rotate;

[0061] Fig.12 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 1;

[0062] Fig.13 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 1;

[0063] Fig.14 This is a test data analysis diagram of the oscillation impact of the prior art solution.

[0064] Figure numerals: a shaft 1, a first support seat 2, a thrust bearing 3, a fixed cone disk of a shaft 4, an annular transmission member 5, a movable cone disk of a shaft 6, a torsion rolling body 7, a thrust rolling body 8, a main thrust disk 9, a main thrust ramp groove 9-1, a secondary thrust ramp groove 9-2, a main torque disk 10, a main torque ramp groove 10-1, a secondary torque ramp groove 10-2, a first elastic component of a shaft 11, a second elastic component of a shaft 12, a second support seat 13, a second shaft 14, a third support seat 15, a first elastic component of a second shaft 16, a movable centrifugal disk 17, a movable centrifugal disk Centrifugal ramp groove 17-1, radial limit portion 18, centrifugal block 19, fixed centrifugal disc 20, fixed centrifugal ramp groove 20-1, speed regulating push rod 21, two-axis dynamic cone disc 22, two-axis fixed cone disc 23, circumferential elastic component 24, power positive rotation direction 25, fourth support seat 26, two-axis second elastic component 27, mechanical gap 28, fifth support seat 29, preload elastic component 30, preload elastic component support seat 2a, thrust steel ball 8a, active ramp disc 9a, active ramp raceway 9a-1, driven ramp raceway 9a-2. DETAILED DESCRIPTION

[0065] 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.

[0066] 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.

[0067] 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.

[0068] Example 1

[0069] like Figure 1 As shown, a continuously variable transmission device with a dynamic cone disc pressurized, wherein the first shaft 1 is used as a driving shaft for power source input, and the second shaft 14 is used as a driven shaft for power source input; it includes a first shaft cone disc unit, a second shaft cone disc unit, a thrust unit, a torque unit and an annular transmission member 5 for transmitting power between the first shaft cone disc unit and the second shaft cone disc unit.

[0070] The one-shaft cone-disc unit comprises a shaft 1, a shaft fixed cone-disc 4 and a shaft movable cone-disc 6. The shaft fixed cone-disc 4 comprises a sleeve manufactured integrally with the cone-disc, and is sleeved on the shaft 1 in an axially movable and circumferentially rotatable manner. The outer ring of the sleeve of the shaft fixed cone-disc 4 is provided with a sliding spline, and the inner ring of the shaft movable cone-disc 6 is provided with a sliding spline, and is sleeved on the shaft sleeve of the shaft fixed cone-disc 4, so that the shaft movable cone-disc 6 and the shaft fixed cone-disc 4 can realize mutual axial movement but not mutual circumferential rotation. The shaft 1 is connected to a power source as an active input shaft.

[0071] One end of the annular transmission member 5 is clamped between the conical surfaces of the fixed cone disk 4 of the first shaft and the movable cone disk 6 of the first shaft, and the non-conical surface end of the fixed cone disk 4 of the first shaft is connected to the outer ring of the thrust bearing 3, and the inner ring of the thrust bearing 3 is sleeved on the first shaft 1 and abuts against the first support seat 2 fixedly connected to the first shaft 1, so that the cone disk unit of the first shaft and the first shaft 1 can achieve mutual rolling rotation, reduce the rotational friction, and limit the axial movement of the fixed cone disk 4 of the first shaft; it is worth emphasizing that the rotation angles of the inner and outer rings of the thrust bearing 3 are the same and synchronous with the rotation angles of the main thrust disk and the movable cone disk of the first shaft, that is, the maximum rotation angle of the thrust bearing 3 will not exceed one circle, and the low mechanical efficiency and poor adaptability will not be caused by high-speed rotation;

[0072] It should be noted that the first support seat 2 and the shaft 1 may be connected in an integral manner, fixed with a locking nut, or in other non-rotatable and non-axially movable manners.

[0073] like Figure 1 and Fig.11 As shown, the thrust unit includes a main thrust plate 9 provided with a main thrust ramp groove 9-1, a thrust rolling body 8 and a first elastic component 11 of a shaft; the main thrust plate 9 is connected to the shaft 1 in an axially movable and circumferentially fixed manner, and the non-ramp groove end surface abuts against a fifth support seat 29 fixedly connected to the shaft 1; the non-conical end surface of the one-shaft movable cone plate 6 is provided with a secondary thrust ramp groove 9-2 matching the main thrust ramp groove 9-1; one end of the first elastic component 11 of the one shaft abuts against the end surface of the main thrust plate 9 and provides pressure toward the one-shaft movable cone plate 6 to the main thrust plate 9, and the other end abuts against the end surface of the main torque plate 10.

[0074] like Fig.11 As shown in FIG. 1 , the secondary thrust ramp groove 9-2 and the main thrust ramp groove 9-1 are both V-shaped slope groove structures that rise symmetrically from the middle to both ends. If adapted to a power source that does not output reverse torque, the secondary thrust ramp groove 9-2 and the main thrust ramp groove 9-1 can be set as a unidirectional slope groove that rises from one end to the other end (such as Figure 4 As shown), that is, there is no need to set a reverse torque pressurizing ramp groove; the secondary thrust ramp groove 9-2 and the main thrust ramp groove 9-1 are arranged symmetrically with the clamped thrust rolling body 8 as the center, so that when the main thrust disc 9 and the one-axis dynamic cone disc 6 transmit torque, an axial thrust will be generated on the one-axis dynamic cone disc 6, and the relative rotation of the main thrust disc 9 and the one-axis dynamic cone disc 6 can provide a speed regulating stroke for the axial movement of the one-axis dynamic cone disc 6; in the installed state, the thrust rolling body 8 sets the secondary thrust ramp groove 9-2 at the lowest point, and the annular transmission member 5 is at the minimum working radius of the one-axis cone disc unit; in this embodiment, a total of 3 groups of secondary thrust ramp grooves 9-2 and main thrust ramp grooves 9-1 are provided, and are evenly arranged along the circumference of the one-axis dynamic cone disc 6.

[0075] like Figure 1 and Fig.11As shown, the torsion unit includes a main torsion plate 10 provided with a main torsion ramp groove 10-1, a torsion rolling body 9 and a second elastic component 12 of a shaft;

[0076] The main torque disc 10 is connected to the shaft 1 through an axial sliding spline; the non-conical end surface of the movable cone disc 6 of the shaft is provided with a secondary torque ramp groove 10-2 matching the main torque ramp groove 10-1; in the installed state, the torsion rolling body 7 is clamped in the middle position between the main torque ramp groove 10-1 and the secondary torque ramp groove 10-2; one end of the second elastic component 12 of the shaft abuts on the end surface of the non-main torque ramp groove 10-1 of the main torque disc 10, and the other end abuts on the second support seat 13 fixedly connected to the shaft 1. It should be noted that the connection method of the second support seat 13 and the shaft 1 can be integrally manufactured, fixed with a locking nut or other non-rotatable and non-axially movable connection methods.

[0077] like Fig.11 As shown, the auxiliary torsion ramp groove 10-2 and the main torsion ramp groove 10-1 are both unidirectional ramp grooves rising from one end to the other end, and the auxiliary torsion ramp groove 10-2 and the main torsion ramp groove 10-1 are arranged symmetrically with the clamped torsion rolling body 7 as the center; the second elastic component 12 of the first axis pushes the main torsion disk 10 to squeeze the torsion rolling body 7 to roll, thereby driving the power source connected to the first axis 1 to rotate forward until the mechanical gap 28 is eliminated, and the annular transmission member 5 forms a preload between the first axis cone disk unit and the second axis cone disk unit.

[0078] In this embodiment, three groups of auxiliary torque ramp grooves 10-2 and main torque ramp grooves 10-1 are provided, and are evenly arranged along the circumference of the one-axis movable cone disc 6; it should be noted that the positions of the thrust unit and the torque unit on the one-axis 1 are not unique, and in other embodiments other than this embodiment, the thrust unit can be arranged on the outside, and the torque unit can be arranged on the inside, which also belongs to the scope of protection of the present invention;

[0079] like Figure 1 As shown, the continuously variable transmission device also includes a two-shaft cone-disk unit and a centrifugal speed regulating unit;

[0080] The two-shaft cone-disk unit comprises two shafts 14, two-shaft fixed cone disks 23 fixedly connected to the two shafts 14, and two-shaft movable cone disks 22 coaxially sleeved on the two shafts 14 through axial sliding splines, so that the two-shaft movable cone disks 22 and the two shafts 14 can move axially relative to each other but are fixed circumferentially;

[0081] The centrifugal speed regulating unit comprises a fixed centrifugal disc 20 provided with a fixed centrifugal ramp groove 20-1, a dynamic centrifugal disc 17 provided with a dynamic centrifugal ramp groove 17-1, a centrifugal block 19 and a first elastic component 16 of the second axis;

[0082] The fixed centrifugal disc 20 is fixedly connected to the two shafts 14, and the non-slope groove end of the fixed centrifugal disc 20 is coaxially arranged with the non-conical surface end of the two-shaft dynamic cone disc 22, and the spacing distance is greater than the axial movement distance of the two-shaft dynamic cone disc 22; the dynamic centrifugal disc 17 is connected to the two shafts 14 through an axial sliding spline so that they can move axially with each other but cannot rotate circumferentially with each other; the dynamic centrifugal slope groove 17-1 and the fixed centrifugal slope groove 20-1 are both unidirectionally rising slope grooves arranged radially along the two shafts 14, and the dynamic centrifugal slope groove 17-1 and the fixed centrifugal slope groove 20-1 are coaxially arranged with each other and clamp the centrifugal block 19; this embodiment is provided with 6 groups of dynamic centrifugal slope grooves 17-1 and fixed centrifugal slope grooves 20-1 clamping the centrifugal block 19.

[0083] The second-axis first elastic component 16 is sleeved on the second axis 14, with one end abutting against the third support seat 15 fixedly connected to the second axis 14, and the other end abutting against the non-slope groove end of the dynamic centrifugal disc 17 and providing pressure; it should be noted that the connection method between the third support seat 15 and the second axis 14 can be integrally manufactured, fixed with a locking nut or other non-rotatable and non-axially movable connection methods;

[0084] The fixed centrifugal disc 20 is evenly provided with three through holes for sleeve-mounting the speed regulating push rods 21 near the inner ring. The three speed regulating push rods 21 pass through the through holes on the fixed centrifugal disc 20, with one end abutting against the slope groove end of the dynamic centrifugal disc 17, and the other end abutting against the non-conical surface end of the two-axis dynamic cone disc 22. The outer sides of the dynamic centrifugal disc 17 and the two-axis dynamic cone disc 22 in contact with the speed regulating push rods 21 are provided with radial limiting portions 18. The function of the radial limiting portions 18 is to prevent the speed regulating push rods 21 from moving radially under the action of centrifugal force and interfering with the through holes on the fixed centrifugal disc 20.

[0085] In the installed state, the length of the speed regulating push rod 21 is set to ensure that the elastic force of the first elastic component 16 of the second shaft does not act on the dynamic cone disk 22 of the second shaft, and the axial position of the dynamic cone disk 22 of the second shaft is limited to ensure that the annular transmission member 5 is at the maximum working radius of the two-shaft cone disk unit; in the process of transmitting torque, the axial thrust generated by the thrust unit acts on the dynamic cone disk 22 of the second shaft through the annular transmission member 5, which is smaller than the elastic force of the first elastic component 16 of the second shaft; when the second shaft 14 rotates at a high speed, the centrifugal force generated by the centrifugal block 19 compresses the first elastic component 16 of the second shaft to generate axial displacement and pushes the dynamic centrifugal disk 17 to move axially, and at the same time, the thrust generated by the thrust unit and the torsion unit will act on the dynamic cone disk 22 of the second shaft through the annular transmission member 5, and push the dynamic cone disk 22 of the second shaft to move axially in the same direction as the dynamic centrifugal disk 17;

[0086] In this embodiment, the first elastic component 11 of one axis is a butterfly spring with three stacked pieces, the second elastic component 12 of one axis is a butterfly spring with five stacked pieces, and the first elastic component 16 of the second axis is a butterfly spring with seven stacked pieces;

[0087] In another embodiment, the speed regulating push rod 21 may also pass through the outer ring of the fixed centrifugal disc 20 (outside of the centrifugal block 19) to achieve the same function.

[0088] Specifically, the angle of the secondary thrust ramp groove, the angle of the main thrust ramp groove, the secondary thrust ramp groove raceway length, the main thrust ramp groove raceway length, the thrust rolling body diameter, the torsion rolling body and the centrifugal body diameters described in this embodiment satisfy the following relationship:

[0089] 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; L1 is the raceway length when the main thrust ramp groove and the secondary thrust ramp groove are V-shaped slope groove structures; R max is the maximum rolling radius of the annular transmission part, R min 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, L1 and d satisfy the following mathematical relationship:

[0090]

[0091] L1≥2*(R max -R min )*tan a1 / 0.9 / sin a2

[0092] d≥(R max -R min )*tan a1*2 / 0.9

[0093] The usage of this structure is as follows:

[0094] This embodiment takes the application of a pure electric vehicle as an example, with the first shaft 1 as the power input shaft and the second shaft 14 as the output shaft as an example, and analyzes the typical working conditions:

[0095] When the vehicle speed is zero and before power is transmitted, the mechanical clearance 28 between the main thrust disc 9 and the first-axis dynamic cone disc 6 has been eliminated by the torque unit driving power source to rotate forward, and the thrust rolling body 8 is located at the position of the secondary thrust ramp groove 9-2 and the main thrust ramp groove 9-1. 0+ / N 0+The torsion rolling element 7 is located at the X position between the secondary torsion ramp groove 10-2 and the primary torsion ramp groove 10-1. 0+ / Y 0+ , the centrifugal rolling body 21 is located at the lowest point H0 / J0 of the dynamic centrifugal ramp groove 17-1 and the fixed centrifugal ramp groove 20-1, at which time the transmission speed ratio is the maximum (such as Fig.11 shown);

[0096] When the vehicle transmits torque and reaches the maximum speed from zero speed, the centrifugal rolling body 21 compresses the first elastic component 16 of the second shaft under the action of centrifugal force and pushes the dynamic centrifugal disc 17 to move axially. At the same time, the thrust generated by the dynamic cone disc 6 of the first shaft under the action of the torque unit and the thrust unit acts on the dynamic cone disc 22 of the second shaft through the annular transmission member 5 to achieve synchronous axial movement speed regulation; at this time, the thrust rolling body 8 is located at the M1 / N2 position of the secondary thrust ramp groove 9-2 and the main thrust ramp groove 9-1, the torsion rolling body 7 is located at the X1 / Y2 position of the secondary torsion ramp groove 10-2 and the main torsion ramp groove 10-1, the second elastic component 12 of the first shaft is extended, and the centrifugal rolling body 21 is located at the highest point H1 / J1 of the dynamic centrifugal ramp groove 17-1 and the fixed centrifugal ramp groove 20-1. At this time, the transmission speed ratio is at the minimum (such as Fig.12 shown).

[0097] When the vehicle switches to the braking energy recovery working condition, the process of the torsional rolling body 7 climbing from position X1 / Y2 to X2 / Y1 will compress the second elastic component 12 of the first axis and provide the clamping force required for transmitting the reverse torque. At the same time, the first elastic component 11 of the first axis pushes the main thrust disc 10 to move axially and presses the thrust rolling body 8 to prevent the thrust rolling body 8 from leaving the thrust ramp groove in this working condition, while satisfying the rolling motion of the thrust rolling body 8 (the thrust provided by the first elastic component 11 of the first axis only needs to meet the thrust of the main thrust disc 10 axially under this working condition). until the thrust rolling element 8 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 12 of the first axis can prevent the thrust rolling element 8 from rushing directly from M1 / N2 to M2 / N1 quickly, causing the annular transmission member 5 to slip and impact. At this time, it is a transient working condition, the vehicle speed has not been reduced in time, the centrifugal block is still in the H1 / J1 position, and the transmission speed ratio is still at the minimum (such as Fig.13 This working process explains the principle of reverse drag transmission of power.

[0098] When the vehicle is moving from the maximum speed (such as Fig.13As the vehicle speed decreases from M2 / N1 to 0 kph, the centrifugal force of the centrifugal rolling element 21 decreases as the vehicle speed decreases, and the centrifugal force falls from the highest position H1 / J1 to the lowest position H0 / J0 under the thrust of the first elastic component 16 of the second shaft. At the same time, the thrust of the first elastic component 16 of the second shaft acts on the second shaft movable cone disc 22 through the speed regulating push rod 21, and is transmitted to the first shaft cone disc unit through the annular transmission member 5. The first shaft movable cone disc 6 squeezes the thrust rolling element 8 from M2 / N1 to M 0+ / N 0+ position, and at the same time pushes the main thrust disc 10 to move axially and compresses the first elastic component 11 of the first axis until the main thrust disc 10 abuts against the fifth support seat 29, and at the same time the torsion rolling body 7 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.11 shown).

[0099] Taking the application of this technology in road vehicles as an example, the comparison principle of the torsion unit in solving impact and the existing technical solutions is analyzed:

[0100] like Figure 8 As shown, it is a connection structure of the prior art solution, in which an active ramp disk 9a provided with an active ramp raceway 9a-1 is axially slidably and circumferentially fixedly connected to a shaft 1, and a non-slope groove end surface of the active ramp disk 9a is pressed and connected with a preload elastic component 30 sleeved on the shaft 1, and the other end of the preload elastic component 30 is sleeved and fixed on the shaft 1, and provides a preload force to the annular transmission member 5; a driven ramp raceway 9a-2 corresponding to the active ramp disk 9a is provided at the non-conical end of the fixed cone disk 4 of the shaft, and a thrust steel ball 8a is clamped in the driven ramp raceway 9a-2 and the active ramp raceway 9a-1; when there is a mechanical gap 28, the thrust steel ball 8a will climb along the ramp raceway when transmitting power, that is, the climbing of the thrust steel ball 8a does not provide a speed regulation stroke, and the speed regulation is achieved by setting an active speed regulation system to control the synchronous and unidirectional movement of the one-shaft dynamic cone disk and the two-shaft dynamic cone disk;

[0101] The principle of impact generation in the existing technical solution is as follows: Figure 8 As shown, when the active ramp raceway 9a-1 and the driven ramp raceway 9a-2 have a mechanical gap 28 with the thrust steel ball 8a; the prior art solution promotes the active ramp disc 9a to move axially to eliminate the mechanical gap 28 (such as Fig. 9 When the power transmission active ramp disk 9a compresses the preload elastic component 30, the rolling element 10a quickly climbs from M0 / N0 to M 0+ / N 0+ position, at which the preload elastic component 30 cannot be compressed (eg Fig.10As shown), the whole vehicle will be impacted; and because of the large inertia of the whole vehicle, at the moment of impact, the speed of the active ramp disk 9a connected to the power source is relatively reduced, causing the thrust steel ball 8a to fall back along the driven ramp raceway 9a-2, and at the same time, the preload elastic component 30 is extended again to eliminate the mechanical gap 28 (as shown in FIG. Fig. 9 When the power is continuously output and the preload elastic component 30 is compressed, the above impact process will continue to occur in an oscillating manner (test analysis data as shown in Fig.14 shown).

[0102] The principle of the torsion unit of the present invention to eliminate impact is as follows: Fig.11 As shown, the elastic pressure of the second elastic component 12 of the first axis on the main torque plate 10 will push the torsion rolling body 7 to roll from the X0 / Y0 position to the X1 / Y2 direction to the X0 / Y0 position. 0+ / Y 0+ position, and at the same time drive the power source to rotate forward until the thrust rolling element 8 climbs from the M0 / N0 position to the M 0+ / N 0+ The position is adjusted until the mechanical clearance 28 is eliminated.

[0103] The core concept of eliminating the mechanical gap 28 of the torque unit of the present invention is to drive the power source to rotate in the positive direction until the mechanical gap 28 is eliminated; that is, the mechanical gap 28 is eliminated before power is transmitted or in the installed state.

[0104] Example 2

[0105] like Figure 5 As shown, a continuously variable transmission device with dynamic cone disc pressurization is disclosed, comprising a first-shaft cone disc unit, a second-shaft cone disc unit, a thrust unit, a torque unit, and an annular transmission member 5 for transmitting power between the first-shaft cone disc unit and the second-shaft cone disc unit; in this embodiment, the first shaft 1 is used as a driven shaft, and the second shaft 14 is used as a driving shaft for inputting a power source;

[0106] The two-shaft cone disk unit comprises two shafts 14 and two-shaft fixed cone disks 23 and two-shaft movable cone disks 22 with coaxial cone surfaces arranged opposite to each other; the two-shaft fixed cone disks 23 are sleeved and fixedly connected with the two shafts 14, and the two-shaft movable cone disks 22 are sleeved and fixedly connected with the two shafts 14 so as to be axially relatively movable.

[0107] Further, the centrifugal speed regulating unit comprises a dynamic centrifugal disc 17, a centrifugal block 19 and a first elastic component 16 of the second shaft, which are arranged on the side of the second shaft fixed cone disc 23; the dynamic centrifugal disc 17 is sleeved on the second shaft 14 in a manner that it can move axially relative to each other but is fixed circumferentially; the opposite end surfaces of the dynamic centrifugal disc 17 and the second shaft fixed cone disc 23 on the non-conical surface side are respectively provided with a dynamic centrifugal slope groove 17-1 and a fixed centrifugal slope groove 20-1, and the dynamic centrifugal slope groove 17-1 and the fixed centrifugal slope groove 20-1 are radially inclined from low to high ramp raceways; in the installed state, the centrifugal block 19 clamps The first elastic component 16 of the second shaft is sleeved on the second shaft 14, and one end is pressed against the dynamic centrifugal disc 17, and the other end is pressed against the third support seat 15 fixedly connected to the second shaft 14; the second elastic component 27 of the second shaft is sleeved on the second shaft 14, and two groups of elastic parts with different elastic coefficients are provided, one end of the second elastic component 27 of the second shaft is pressed against the non-conical end of the dynamic cone disc 22 of the second shaft, and the other end is axially fixed through the fourth support seat 26 sleeved and fixedly connected to the second shaft 14;

[0108] Furthermore, the two-shaft fixed cone disc 23 is provided with three through holes near the sleeve portion, and the speed regulating push rod 21 passes through the through holes to abut and connect the dynamic centrifugal disc 17 with the two-shaft dynamic cone disc 22, and the abutting portions are provided with groove-shaped radial limiting portions 18 to limit the radial position of the speed regulating push rod 21;

[0109] Further, the centrifugal speed regulating unit is provided with 6 groups of dynamic centrifugal ramp grooves 17-1 and fixed centrifugal ramp grooves 20-1 clamping the centrifugal block 19; the maximum elastic coefficient of the two-axis first elastic component 16 is greater than the maximum elastic coefficient of the two-axis second elastic component 27, and in the installed state, the two-axis first elastic component 16 limits the axial position of the two-axis dynamic cone disk 22 through the speed regulating push rod 21, so that the annular transmission member 5 is at the minimum working radius of the two-axis cone disk unit;

[0110] The one-shaft cone-disk unit comprises an axis 1, an axis fixed cone-disk 4 and an axis movable cone-disk 6, the other end of the annular transmission member 5 is clamped between the conical surfaces of the one-shaft cone-disk unit; the one-shaft fixed cone-disk 4 comprises a sleeve integrally manufactured with the cone-disk, and is sleeved on the one-shaft 1 in an axially movable and circumferentially rotatable manner, the sleeve outer ring of the one-shaft fixed cone-disk 4 is provided with a sliding spline, the inner ring of the one-shaft movable cone-disk 6 is provided with a sliding spline, and is sleeved on the sleeve of the one-shaft fixed cone-disk 4, so that the one-shaft movable cone-disk 6 and the one-shaft fixed cone-disk 4 can realize mutual axial movement but cannot realize mutual circumferential rotation; the one-shaft fixed cone The non-conical end of the disk 4 is connected to the outer ring of the thrust bearing 3, and the inner ring of the thrust bearing 3 is sleeved on the shaft 1 and rests on the first support seat 2 fixedly connected to the shaft 1, so that the shaft cone disk unit and the shaft 1 can achieve mutual rolling rotation, reducing the rotational friction and limiting the axial movement of the shaft fixed cone disk 4; it is worth emphasizing that the rotation angles of the inner and outer rings of the thrust bearing 3 are the same and synchronized with the rotation angles of the main thrust disk 9 and the shaft movable cone disk 6, that is, the maximum rotation angle of the thrust bearing 3 will not exceed one circle, and low mechanical efficiency and poor adaptability will not be caused by high-speed rotation.

[0111] Further, the thrust unit includes a main thrust disc 9, a thrust rolling body 8 and a first elastic component 11 of a shaft; the main thrust disc 9 is sleeve-connected with the shaft 1 in a circumferentially fixed manner by axial movement, the end face of the main thrust disc 9 is against a fifth support seat 29 fixedly connected to the shaft 1, and the outer ring of the main thrust disc 9 is provided with a sliding spline; the main thrust disc 9 and the non-conical end of the shaft movable cone disc 6 are respectively provided with a main thrust ramp groove 9-1 and a secondary thrust ramp groove 9-2, the secondary thrust ramp groove 9-2 and the main thrust ramp groove 9-1 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 9-2 and the main thrust ramp groove 9-1 are respectively provided with a V-shaped ramp groove that rises symmetrically from the low point to both ends in the circumferential direction. The ramp groove 9-1 is arranged symmetrically with the clamped thrust rolling body 8 as the center; the first elastic component 11 of the first shaft is sleeved on the first shaft 1, one end of which presses against the end face of the main thrust disc 9, and the other end presses against the second support seat 13 which is sleeved and fixedly connected with the first shaft 1. When the power source switches from transmitting the positive driving torque to transmitting the reverse drag torque (such as electric vehicle braking energy recovery), the first elastic component 11 of the first shaft pushes the main thrust disc 9 to move axially and press the thrust rolling body 8 to prevent the thrust rolling body 8 from leaving the thrust ramp groove in this working condition, that is, the main effect of the first elastic component 11 of the first shaft is to ensure that the thrust rolling body 8 can work normally in the process of switching to the reverse drag working condition;

[0112] Further, the thrust unit is provided with three groups of secondary thrust ramp grooves 9-2 and main thrust ramp grooves 9-1 clamping the thrust rolling body 8; in the installed state, the thrust rolling body 8 is arranged in the main thrust ramp groove 7-1 in the positive driving torque direction of the power source, and the axial displacement from the highest point of the main thrust ramp groove 7-1 is 3mm;

[0113] Further, the torsion unit comprises a main torsion plate 10, a torsion rolling body 7 and a second elastic component 12 of a shaft; the inner ring of the main torsion plate 10 is provided with a sliding spline and is sleeved on the outer ring spline of the main thrust plate 9, so as to realize axial movement with the shaft 1 but circumferential fixed connection; the opposite end surfaces of the main torsion plate 10 and the non-conical end of the shaft movable cone plate 6 are respectively provided with a main torsion ramp groove 10-1 and a secondary torsion ramp groove 10-2; the main torsion ramp groove 10-1 and the secondary torsion ramp groove 10-2 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 7 as the center;

[0114] The first-axis second elastic component 12 is sleeved on the first-axis 1, with one end pressed against the end surface of the main torque disc 10, and the other end pressed against the second support seat 13 sleeved and fixedly connected to the first-axis 1. The first-axis second elastic component 12 pushes the main torque disc 10 to squeeze the torsion rolling body 7 to roll, thereby driving the power source connected to the first-axis 1 to rotate forward until the mechanical gap 28 is eliminated, and the annular transmission member 5 forms a preload between the first-axis cone disc unit and the second-axis cone disc unit;

[0115] Furthermore, the torsion unit is provided with three groups of auxiliary torsion ramp grooves 7-1 and main torsion ramp grooves 10-1 clamping the torsion rolling body 7; in the installed state, the torsion rolling body 7 is arranged in the middle position of the auxiliary torsion ramp groove 12-1, and the first-axis second elastic component 12 limits the annular transmission component 5 to the maximum working radius state of the first-axis cone disk unit; the elastic coefficient of the first-axis second elastic component 12 is less than the minimum elastic coefficient of the second-axis second elastic component 27.

[0116] In the installed state, the annular transmission member 5 is at the minimum working radius position of the two-axis cone disk unit, the thrust of the second elastic component 27 of the two axes does not act on the annular transmission member 5, and the preload force of the system is provided by the torque unit.

[0117] Example 3

[0118] like Figure 2 and Figure 3 As shown, this embodiment is an alternative structure of the torsion unit, and the difference from the first embodiment is that the torsion unit is provided with a circumferential elastic component 24 between the main torsion plate 10 and the one-axis dynamic cone plate 6 to replace the auxiliary torsion ramp groove 10-2, the torsion rolling body 7 and the main torsion ramp groove 10-1, thereby realizing the provision of positive rotation torque to the power source.

[0119] Example 4

[0120] This embodiment discloses a hybrid vehicle equipped with the continuously variable transmission device in Embodiment 1, wherein a shaft 1 is connected to the motor output end of the vehicle, and a shaft 14 is connected to the wheel end of the vehicle. The transmission ratio can be adaptively adjusted by changing the wheel speed.

[0121] Example 5

[0122] This embodiment discloses a three-wheeled or two-wheeled motorcycle equipped with the continuously variable transmission device in Embodiment 1, wherein the first shaft 1 is connected to the power source output end, and the second shaft 14 is connected to the wheel end. The transmission speed ratio can be adaptively adjusted by changing the wheel rotation speed.

[0123] Example 6

[0124] This embodiment discloses a wind turbine gearbox equipped with the continuously variable transmission device in Embodiment 1, wherein a shaft 1 is connected to the rotating shaft on which the wind wheel (blades) is installed, and a second shaft 14 is connected to the rotating shaft of the generator. The torque generated when the wind wheel rotates can be amplified by the continuously variable transmission in this embodiment, thereby reducing the minimum wind speed for starting the generator.

[0125] 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 device with a dynamic cone disc pressurized, comprising a one-shaft cone disc unit, a two-shaft cone disc unit, and an annular transmission member for connecting the one-shaft cone disc unit and the two-shaft cone disc unit, wherein the one-shaft cone disc unit comprises a shaft, a one-shaft fixed cone disc and a one-shaft dynamic cone disc; the one-shaft fixed cone disc is sleeved on the one shaft in a manner that they can rotate with each other and are fixed in at least one axial direction, and the one-shaft dynamic cone disc is sleeved on the one-shaft fixed cone disc in a manner that is fixed in the circumferential direction and slidable in the axial direction; the two-shaft cone disc unit comprises two shafts and two-shaft fixed cone discs and two-shaft dynamic cone discs with cone surfaces arranged opposite to each other; and a power source is connected to the one shaft or the two shafts, characterized in that: Also includes thrust unit and torque unit; The thrust unit comprises a thrust rolling body and a main thrust disc arranged on the non-conical surface side of a shaft-moving cone disc, the main thrust disc is connected to a shaft in a circumferentially fixed and axially movable manner, the main thrust disc and the non-conical surface end of the shaft-moving cone disc are respectively provided with a main thrust ramp groove and a secondary thrust ramp groove which are centrally symmetrical with respect to clamping the thrust rolling body, so that when the main thrust disc and the shaft-moving cone disc transmit torque, an axial thrust can be generated on the shaft-moving cone disc, and the clamping force required for the annular transmission member to transmit torque is formed, and the axial stroke generated by the mutual rotation between the main thrust disc and the shaft-moving cone disc matches the axial stroke required for the speed regulation of the shaft-moving cone disc; The torque unit comprises a main torque plate which is sleeved on the one shaft in an axially sliding and circumferentially fixed manner, and the main torque plate is used to provide a forward rotation torque to the power source.

2. The continuously variable transmission device with dynamic cone disc pressurization according to claim 1, characterized in that: The torsion unit also includes a torsion rolling body and a shaft second elastic component; The main torque disc is arranged on one side of the non-conical surface end of a shaft-moving cone disc, and a main torque ramp groove and a secondary torque ramp groove are respectively provided in the circumferential direction of the main torque disc and the non-conical surface end of the shaft-moving cone disc, which are symmetrically distributed around the center of the torsion rolling body. Both the main torque ramp groove and the secondary torque ramp groove are unidirectional ramp grooves that rise from one end to the other end, and at least two groups of secondary torque ramp grooves and main torque ramp grooves that are evenly distributed along the circumferential direction are provided; One end of the second elastic component of the first shaft abuts against the end surface of the main torque disc on the side away from the main torque ramp groove and provides the main torque disc with axial pressure toward the auxiliary torque ramp groove.

3. The continuously variable transmission device with dynamic cone disc pressurization according to claim 2, characterized in that: The thrust unit further comprises a first elastic component of an axis, the first elastic component of an axis is sleeved on an axis and arranged on a side of the main thrust disc away from the first axis movable cone disc, so as to provide an axial thrust to the main thrust disc in a direction toward the first axis movable cone disc, and an end surface of the main thrust disc away from the first axis movable cone disc abuts against a fifth support seat fixedly connected to the first axis; At least two groups of auxiliary thrust ramp grooves and main thrust ramp grooves are evenly distributed along the circumferential direction of the main thrust disc, and the auxiliary thrust ramp grooves and main thrust ramp grooves are both V-shaped slope groove structures that rise symmetrically from a low point to both ends or unidirectional slope grooves that rise from one end to the other end.

4. The continuously variable transmission device with dynamic cone disc pressurization according to claim 3 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 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 minimum working radius in the one shaft cone disk unit.

5. The continuously variable transmission device with dynamic cone disc pressurization according to claim 3 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 a position close to 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 maximum working radius in a single-axis cone disk unit.

6. The continuously variable transmission device with dynamic cone disc pressurization according to claim 3, characterized in that: It also includes a centrifugal speed regulating unit; the two-shaft fixed cone disc is fixedly connected to the two-shaft sleeve, and the two-shaft movable cone disc is connected to the two-shaft sleeve in a circumferentially fixed and axially movable manner; The centrifugal speed regulation unit includes a dynamic centrifugal disc, a fixed centrifugal disc, a centrifugal block and a first elastic component of two shafts. The dynamic centrifugal disc is abutted against the dynamic cone discs of the two shafts, and the first elastic component of the two shafts is abutted against the dynamic centrifugal disc. The axially opposite end faces 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 centrifugal block is clamped between the dynamic centrifugal slope groove and the fixed centrifugal slope groove. Under the action of the rotating centrifugal force, the centrifugal block compresses the first elastic component of the two shafts and causes the dynamic centrifugal disc to move axially, while providing space for synchronous and unidirectional axial movement of the dynamic cone discs of the two shafts for speed regulation.

7. The continuously variable transmission device with dynamic cone disc pressurization according to claim 6, characterized in that: The dynamic centrifugal ramp groove and the fixed centrifugal ramp groove are radially inclined ramp raceways from low to high, and at least two groups of dynamic centrifugal ramp grooves and fixed centrifugal ramp grooves are evenly distributed along the circumferential direction to clamp the centrifugal body.

8. The continuously variable transmission device with dynamic cone disc pressurization according to claim 6, characterized in that: When the one shaft is connected to the power source and serves as the driving shaft, the fixed centrifugal disc is fixedly sleeved on the two shafts and arranged on one side of the non-conical surface end of the dynamic conical disc of the two shafts, and the dynamic centrifugal disc is sleeved on the two shafts in an axially movable and circumferentially fixed manner and arranged on the side of the fixed centrifugal disc away from the dynamic conical disc of the two shafts; The fixed centrifugal disc is provided with a through hole, so that the non-conical end of the two-axis dynamic cone 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 two-shaft cone disk unit, and in the process of transmitting torque, the axial thrust generated by the thrust unit acts on the two-shaft dynamic cone disk through the annular transmission member. The thrust is smaller than the elastic force of the first elastic component of the two shafts.

9. The continuously variable transmission device with dynamic cone disc pressurization according to claim 6, characterized in that: When the two shafts are connected to a power source and serve as driving shafts, the centrifugal speed regulating unit further includes a second elastic component of the two shafts; One end of the second elastic component of the second shaft is fixedly connected to the second shaft sleeve, and the other end is pressed against the non-conical surface end of the movable cone disk of the second shaft, and provides a thrust to the movable cone disk of the second shaft toward the fixed cone disk of the second shaft. The second elastic component of the second 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 second shaft is smaller than the elastic coefficient of the first elastic component of the second shaft; The dynamic centrifugal disk 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 fixed conical disk of the two shafts. The fixed centrifugal disk is fixedly connected with the non-conical surface end of the fixed conical disk of the two shafts or is integrally formed and manufactured, and is arranged on one side of the dynamic centrifugal disk close to the fixed conical disk of the two shafts; The two-shaft fixed conical disc and the fixed centrifugal disc are both provided with through holes, and the dynamic centrifugal disc abuts against the two-shaft dynamic conical disc via a speed regulating push rod passing through the through holes; In the installed state, the first elastic component of the second shaft compresses the second elastic component of the second shaft through the speed regulating push rod, and ensures that the annular transmission member is at the minimum working radius of the second shaft cone disk unit.

10. The continuously variable transmission device with dynamic cone disc pressurization according to claim 9, 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">L1≥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 <h2 style=";text-align:left;direction:ltr">L2≥(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; L1 is the raceway length when the main thrust ramp groove and the secondary thrust ramp groove are V-shaped slope groove structures; L2 is the raceway length when the main thrust ramp groove and the secondary thrust ramp groove are unidirectional slope grooves that rise from one end to the other end; 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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