Mechanical continuously variable transmission and method of use thereof

Abstract

The application provides a mechanical continuously variable transmission and a use method thereof in the field of continuously variable transmissions, and the mechanical continuously variable transmission comprises a driving assembly, and the driving assembly comprises a movable frame, a fixed frame, a first cross universal coupling and a second cross universal coupling; the application mainly comprises two cross universal couplings with a phase difference of 90 degrees, a differential and a gear one-way clutch, the unevenness of the output speed of the cross universal couplings is utilized, two fluctuation speeds with a phase difference of 90 degrees generated by the two cross universal couplings with a phase difference of 90 degrees are adopted, the differential is used to differentially output the speeds of the two cross universal couplings, and then the gear one-way clutch is used to make the differential become continuous output; the change of the shaft included angle of the two cross universal couplings can change the speed transmission ratio, and realizes stepless speed change. The mechanical continuously variable transmission has simple transmission structure, high transmission efficiency, can meet the flexible speed adjustment, and has high speed change transmission precision.

Description

Technical Field

[0001] This invention belongs to the field of continuously variable transmissions (CVTs), and specifically relates to a mechanical CVT and its usage method. Background Technology

[0002] A continuously variable transmission (CVT) is a transmission device that can steplessly adjust the output speed, achieving stepless gear shifting of the drive wheels through different mechanisms and principles. Its main function is to provide optimal power output at different speeds, improving fuel economy and driving comfort in automobiles.

[0003] Currently, the most common continuously variable transmissions (CVTs) in the industry include steel belt CVTs and crank-slider CVTs. Steel belt CVTs have problems such as high frictional heat generation, low torque capacity, and easy fatigue leading to reduced service life. CVTs with crank-slider structures are large in size and have problems such as high mechanical noise and vibration due to rotational eccentricity. Summary of the Invention

[0004] This embodiment aims to at least partially solve one of the technical problems in related technologies. This invention provides a mechanical continuously variable transmission (CVT) and its usage method, which features low noise, low vibration, no frictional heat generation, and adaptability to harsh environments through a purely mechanical drive. It also boasts advantages such as compact structure, small size, high transmission efficiency, long service life, and convenient maintenance. The specific solution is as follows:

[0005] A mechanical continuously variable transmission includes a drive assembly, a first bevel gear, and a second bevel gear;

[0006] The driving component includes:

[0007] A movable frame and a fixed frame, wherein the movable frame and the fixed frame are arranged in parallel relative to each other;

[0008] A first universal joint and a second universal joint are provided. One end of the first universal joint is mounted on the movable frame, and the other end is mounted on the fixed frame. One end of the second universal joint is mounted on the movable frame, and the other end is mounted on the fixed frame. The first universal joint and the second universal joint are arranged with a 90° phase angle difference and are parallel to each other.

[0009] An input shaft is connected to an end shaft mounted on the movable frame by the second universal joint.

[0010] The first synchronizing gear is mounted on the end shaft of the first universal joint coupling mounted on the movable frame.

[0011] A second synchronizing gear is mounted on the input shaft;

[0012] An intermediate gear is mounted on the movable frame, and a synchronizing gear is disposed between the first synchronizing gear and the second synchronizing gear. The intermediate gear meshes with both the first synchronizing gear and the second synchronizing gear.

[0013] Wherein, the first bevel gear is installed on the end shaft of the first universal joint mounted on the fixed frame, and the second bevel gear is installed on the end shaft of the second universal joint mounted on the fixed frame;

[0014] The central axes of the first bevel gear and the second bevel gear are arranged in parallel, and the drive assembly drives the first bevel gear and the second bevel gear to rotate in the same direction.

[0015] Optionally, the device further includes a differential, which includes: a first planetary gear, a second planetary gear, a first drive gear, a second drive gear, a first planetary carrier gear, a second planetary carrier gear, a differential planetary carrier, a first differential bevel gear, and a second differential bevel gear;

[0016] The bottom of the first differential bevel gear and the second differential bevel gear mesh, the top of the second differential bevel gear and the first differential bevel gear mesh, the central axis of the first differential bevel gear coincides with the central axis of the second differential bevel gear, the central axis of the second differential bevel gear is perpendicular to the central axis of the second differential bevel gear, and the differential planetary carrier is disposed between the first differential bevel gear and the second differential bevel gear.

[0017] When the input shaft rotates, the first bevel gear and the second bevel gear rotate in the same direction, while the first differential bevel gear and the second differential bevel gear rotate in opposite directions.

[0018] Wherein, the first planetary carrier gear is mounted on the differential planetary carrier and is arranged on the same side as the first differential bevel gear, the first bevel gear is connected to the first drive wheel, and the first bevel gear drives the first drive wheel to rotate in the same direction;

[0019] The second planetary carrier gear is mounted on the differential planetary carrier and is located on the same side as the second differential bevel gear; the second bevel gear is connected to the second drive wheel, and the second bevel gear drives the second drive wheel to rotate in the same direction.

[0020] The first planetary gear, the second planetary gear, the first drive gear, and the second drive gear are installed in the differential planetary carrier.

[0021] One side of the first planetary gear meshes with one side of the first driving gear, and the other side of the first planetary gear meshes with one side of the second driving gear;

[0022] One side of the second planetary gear meshes with the other side of the first driving gear, and the other side of the second planetary gear meshes with the other side of the second driving gear;

[0023] The second differential bevel gear is connected to the first drive gear via a first connector, and the first connector passes through the first planetary carrier gear;

[0024] The first differential bevel gear is connected to the second drive gear via a second connector, and the second connector passes through the second planetary carrier gear;

[0025] Wherein, the first connector and the second connector are on the same axis;

[0026] When the input shaft rotates in the forward direction, the first universal joint and the second universal joint output angular velocities with a speed difference. The first universal joint drives the first bevel gear to rotate in the forward direction, and the second universal joint drives the second bevel gear to rotate in the forward direction. The first differential bevel gear and the second differential bevel gear rotate in opposite directions.

[0027] When the rotational speed of the first differential bevel gear is equal to the rotational speed of the second differential bevel gear, the first planetary gear and the second planetary gear output forces of equal magnitude and opposite direction.

[0028] When the rotational speed of the second differential bevel gear is greater than the rotational speed of the first differential bevel gear, the differential rotates in the first direction around the first connecting member and the second connecting member;

[0029] When the rotational speed of the second differential bevel gear is less than the rotational speed of the first differential bevel gear, the differential rotates in a second direction around the first connecting member and the second connecting member.

[0030] Optionally, the continuously variable transmission further includes: a first gear clutch assembly, a second gear clutch assembly, and an intermediate double gear set;

[0031] The first gear clutch assembly includes: a first clutch bevel gear and a first one-way clutch;

[0032] The first one-way clutch is mounted on the first clutch bevel gear, and the first clutch bevel gear supports meshing with the first planetary carrier gear.

[0033] The second gear clutch assembly includes: a second clutch bevel gear and a second one-way clutch;

[0034] The second one-way clutch is mounted on the second clutch bevel gear, which supports meshing with the bevel gear of the intermediate double gear set. The spur gear of the intermediate double gear set meshes with the second planetary carrier gear. When the spur gear of the intermediate double gear set rotates, the spur gear of the intermediate double gear set drives the bevel gear of the intermediate double gear set to rotate in the same direction.

[0035] Optionally, the continuously variable transmission further includes: an output shaft;

[0036] The output shaft is disposed on the central axis of the first clutch bevel gear and the second clutch bevel gear;

[0037] When the rotational speed of the first differential bevel gear is equal to the rotational speed of the second differential bevel gear, the output shaft does not rotate;

[0038] When the rotational speed of the first differential bevel gear is greater than the rotational speed of the second differential bevel gear, the output shaft rotates in the opposite direction;

[0039] When the rotational speed of the first differential bevel gear is less than the rotational speed of the second differential bevel gear, the output shaft rotates in the opposite direction.

[0040] A method of using a mechanical continuously variable transmission (CVT), applied to the aforementioned mechanical CVT, comprising the following method:

[0041] The input shaft is driven to rotate in the forward direction, and the input shaft drives the second synchronous gear to rotate in the same direction. The second synchronous gear drives the first synchronous gear to rotate in the forward direction through the intermediate gear.

[0042] The first synchronous gear drives the first universal joint to rotate in the forward direction, and the second synchronous gear drives the second universal joint to rotate in the forward direction. There is a speed difference between the angular velocity output by the first universal joint and the angular velocity output by the second universal joint.

[0043] The first bevel gear drives the second differential bevel gear to rotate, and the second bevel gear drives the first differential bevel gear to rotate. The first bevel gear and the second bevel gear rotate in the same direction, and the rotation direction of the second differential bevel gear is opposite to that of the first differential bevel gear.

[0044] The second differential bevel gear drives the first drive wheel to rotate, and the first differential drives the second drive wheel to rotate. The rotation direction of the first drive wheel is opposite to the rotation direction of the second drive wheel.

[0045] Specifically, when the rotational speed of the first driving wheel is equal to the rotational speed of the second driving wheel, the output shaft does not rotate;

[0046] Otherwise, the output shaft will rotate in the opposite direction.

[0047] The beneficial effects of the technical solutions provided in the embodiments of the present invention include at least the following:

[0048] This device and method generate differential speed solely through rotation, eliminating eccentric inertia and effectively avoiding the technical problems present in existing technologies. This invention innovatively employs a purely mechanical transmission principle, primarily utilizing a combination of two universal joints with a 90° phase difference, a differential, and a one-way gear clutch. The transmission structure is simple, highly efficient, and can meet the demands for flexible speed adjustment, high transmission accuracy, and large reduction ratios. Furthermore, it is easy to manufacture, has low operating and maintenance costs, a small footprint, and can adapt to harsh environments, making it worker-friendly and possessing extremely high application prospects and value. Attached Figure Description

[0049] To more clearly illustrate the technical solutions in the embodiments of the present invention, the accompanying drawings used in the description of the embodiments will be briefly introduced below. Obviously, the accompanying drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0050] Figure 1 This is a schematic diagram of the device;

[0051] Figure 2 This is a schematic diagram showing that the input shaft of this device rotates in the forward direction;

[0052] Figure 3 This is the schematic diagram of the differential of this device;

[0053] Figure 4 This is a schematic diagram of the universal joint principle of this device;

[0054] Figure 5 This is a schematic diagram showing the angular velocities of the first universal joint, the second universal joint, and the output shaft when the included angle α of the universal joint shaft is 20°.

[0055] Figure 6 This is a schematic diagram showing the angular velocities of the first universal joint, the second universal joint, and the output shaft when the included angle α of the universal joint shaft is 35°.

[0056] Figure 7 This is a schematic diagram showing the angular velocities of the first universal joint, the second universal joint, and the output shaft when the included angle α of the universal joint shafts is 0°.

[0057] Figure 8 This is a schematic diagram of the first and second directions.

[0058] Marker explanation:

[0059] 1. First universal joint; 2. Second universal joint; 3. First synchronizing gear; 4. Second synchronizing gear; 5. Input shaft; 6. Intermediate gear; 7. Fixed frame; 8. First bevel gear; 9. Differential; 9-1. First planetary carrier gear; 9-2. Second planetary carrier gear; 9-3. First differential bevel gear; 9-4. Second differential bevel gear; 9-5. First planetary gear; 9-6. Second planetary gear; 9-7. First drive gear; 9-8. Second drive gear; 9-9. First connecting piece; 9-10. Second connecting piece; 10-1. First clutch bevel gear; 10-2. First one-way clutch; 11-1. Second clutch bevel gear; 11-2. Second one-way clutch; 12. Intermediate double gear set; 13. Output shaft; 14. Movable frame; 15. Second bevel gear. Detailed Implementation

[0060] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of the present invention. All other embodiments obtained by those skilled in the art based on the described embodiments of the present invention without creative effort are within the scope of protection of the present invention.

[0061] Unless otherwise defined, the technical or scientific terms used in this invention shall have the ordinary meaning understood by one of ordinary skill in the art to which this invention pertains. The terms “first,” “second,” and similar terms used in this invention do not indicate any order, quantity, or importance, but are merely used to distinguish different components. Similarly, the terms “an,” “a,” or “the,” and similar terms do not indicate a quantity limitation, but rather indicate the presence of at least one. The terms “comprising,” “including,” or “including,” and similar terms mean that the element or object preceding the word encompasses the element or object listed following the word and its equivalents, without excluding other elements or objects. The terms “connected,” “linked,” or “connected,” and similar terms are not limited to physical or mechanical connections, but can include electrical connections, whether direct or indirect.

[0062] It should be noted that the terms "up", "down", "left", "right", "front", and "back" used in this invention are only used to indicate relative positional relationships. When the absolute position of the object being described changes, the relative positional relationship may also change accordingly.

[0063] This invention relates to a mechanical continuously variable transmission (CVT) and its usage method, suitable for fields requiring a wide range of speed changes. It has low environmental requirements and exhibits stable performance even in harsh environments. For example, it can be applied to transmissions in heavy machinery such as those used in coal mines, which require large reduction ratios. The traction unit of a coal mining machine is responsible for both traction and movement, and its heavy workload necessitates a small-volume transmission. Furthermore, due to the harsh external working environment, high reliability is required for the transmission. Only in this way can the coal mining output be guaranteed while simultaneously increasing the utilization rate of the coal mining machine and reducing equipment maintenance costs.

[0064] This invention is also applicable to automated production lines such as textile machinery. Automated production lines in textile machinery require a transmission device that allows for flexible speed adjustment and easy operation. This means that the driving force and operating speed of the transmission should be changed without altering the engine torque and speed, and the transmission should move forward or backward while maintaining the engine shaft's rotation direction. In this specific scenario, existing transmissions suffer from poor transmission accuracy, high maintenance costs, large space requirements, and significant impact on worker health due to strong vibrations during operation. To address these drawbacks, a new type of transmission device is urgently needed to replace existing devices. Based on these reasons, this invention provides a mechanical continuously variable transmission (CVT) and its usage method, applicable to the aforementioned field, and also to automated production lines in other fields requiring large reduction ratio transmissions.

[0065] Specifically, it includes: a mechanical continuously variable transmission, comprising a drive assembly, a first bevel gear 8, and a second bevel gear 15;

[0066] The driving component includes:

[0067] The movable frame 14 and the fixed frame 7 are arranged in parallel relative to each other.

[0068] A first universal joint 1 and a second universal joint 2 are provided. One end of the first universal joint 1 is mounted on the movable frame 14, and the other end is mounted on the fixed frame 7. One end of the second universal joint 2 is mounted on the movable frame 14, and the other end is mounted on the fixed frame 7. The first universal joint 1 and the second universal joint 2 are provided with a 90° phase angle difference and are arranged in parallel.

[0069] Input shaft 5, which is connected to the end shaft of the second universal joint 2 mounted on the movable frame 14;

[0070] The first synchronous gear 3 is mounted on the end shaft of the first universal joint 1 mounted on the movable frame 14.

[0071] The second synchronizing gear 4 is mounted on the input shaft 5;

[0072] Intermediate gear 6, the mounting shaft of the intermediate gear 6 is mounted on the movable frame 14, the synchronous gear is disposed between the first synchronous gear 3 and the second synchronous gear 4, and the intermediate gear 6 meshes with the first synchronous gear 3 and the second synchronous gear 4 respectively;

[0073] Wherein, the first universal joint 1 is mounted on the end shaft of the fixed frame 7 and the first bevel gear 8 is mounted on the end shaft of the second universal joint 2, which is mounted on the fixed frame 7 and the second bevel gear 15 is mounted on the end shaft of the fixed frame 7;

[0074] The central axes of the first bevel gear 8 and the second bevel gear 15 are arranged in parallel, and the driving component drives the first bevel gear 8 and the second bevel gear 15 to rotate in the same direction.

[0075] This continuously variable transmission also includes a differential 9, which includes: a first planetary gear 9-5, a second planetary gear 9-6, a first drive wheel 9-7, a second drive wheel 9-8, a first planetary carrier gear 9-1, a second planetary carrier gear 9-2, a differential planetary carrier, a first differential bevel gear 9-3, and a second differential bevel gear 9-4.

[0076] The bottom of the first differential bevel gear 9-3 and the second bevel gear 15 are engaged, the top of the second differential bevel gear 9-4 and the first bevel gear 8 are engaged, the central axis of the first differential bevel gear 9-3 coincides with the central axis of the second differential bevel gear 9-4, the central axis of the second differential bevel gear 9-4 is perpendicular to the central axis of the second bevel gear 15, and the differential planetary carrier is disposed between the first differential bevel gear 9-3 and the second differential bevel gear 9-4.

[0077] When the input shaft 5 rotates, the first bevel gear 8 and the second bevel gear 15 rotate in the same direction, while the first differential bevel gear 9-3 and the second differential bevel gear 9-4 rotate in opposite directions.

[0078] Wherein, the first planetary carrier gear 9-1 is mounted on the differential planetary carrier and is arranged on the same side as the first differential bevel gear 9-3, the first bevel gear 8 is connected to the first drive wheel 9-7, and the first bevel gear 8 drives the first drive wheel 9-7 to rotate in the same direction.

[0079] The second planetary carrier gear 9-2 is mounted on the differential planetary carrier and is located on the same side as the second differential bevel gear 9-4; the second bevel gear 15 is connected to the second drive wheel 9-8, and the second bevel gear 15 drives the second drive wheel 9-8 to rotate in the same direction.

[0080] The first planetary gear 9-5, the second planetary gear 9-6, the first drive gear 9-7, and the second drive gear 9-8 are installed in the differential planetary carrier;

[0081] One side of the first planetary gear 9-5 meshes with one side of the first driving gear 9-7, and the other side of the first planetary gear 9-5 meshes with one side of the second driving gear 9-8;

[0082] One side of the second planetary gear 9-6 meshes with the other side of the first driving gear 9-7, and the other side of the second planetary gear 9-6 meshes with the other side of the second driving gear 9-8;

[0083] The second differential bevel gear 9-4 is connected to the first drive gear 9-7 via the first connector 9-9, and the first connector 9-9 passes through the first planetary carrier gear 9-1;

[0084] The first differential bevel gear 9-3 is connected to the second drive gear 9-8 via the second connector 9-10, and the second connector 9-10 passes through the second planetary carrier gear 9-2;

[0085] Wherein, the first connecting member 9-9 and the second connecting member 9-10 are on the same axis;

[0086] When the input shaft 5 rotates in the forward direction, the first universal joint 1 and the second universal joint 2 output angular velocities with a speed difference. The first universal joint 1 drives the first bevel gear 8 to rotate in the forward direction, and the second universal joint 2 drives the second bevel gear 15 to rotate in the forward direction. The first differential bevel gear 9-3 and the second differential bevel gear 9-4 rotate in opposite directions.

[0087] When the rotational speed of the first differential bevel gear 9-3 is equal to the rotational speed of the second differential bevel gear 9-4, the first planetary gear 9-5 and the second planetary gear 9-6 output forces of equal magnitude and opposite direction.

[0088] For the first and second directions, such as Figure 8 As shown, Figure 8 Taking the second connector as an example, the actual rotation structure of the first connector end is synchronized with the second connector. Figure 8 This is a side view of the second connector.

[0089] When the rotational speed of the second differential bevel gear 9-4 is greater than the rotational speed of the first differential bevel gear 9-3, the differential planetary carrier rotates in the first direction around the first connecting member and the second connecting member;

[0090] When the rotational speed of the second differential bevel gear 9-4 is less than the rotational speed of the first differential bevel gear 9-3, the differential planetary carrier rotates in the second direction around the first connecting member and the second connecting member.

[0091] Because the rotational speed of the second differential bevel gear 9-4 was greater than that of the first differential bevel gear 9-3 at the previous moment, and the rotational speed of the second differential bevel gear 9-4 was less than that of the first differential bevel gear 9-3 at the next moment, the entire differential will swing back and forth.

[0092] The continuously variable transmission further includes: a first gear clutch assembly, a second gear clutch assembly, and an intermediate double gear set 12;

[0093] The first gear clutch assembly includes: a first clutch bevel gear 10-1 and a first one-way clutch 10-2; the first one-way clutch 10-2 is disposed on the first clutch bevel gear 10-1, and the first clutch bevel gear supports meshing with the first planetary carrier gear 9-1;

[0094] The second gear clutch assembly includes: a second clutch bevel gear 11-1 and a second one-way clutch 11-2; the second one-way clutch 11-2 is disposed on the second clutch bevel gear 11-1, the first clutch bevel gear supports meshing with the bevel gear of the intermediate double gear set 12, the spur gear of the intermediate double gear set 12 meshes with the second planetary carrier gear 9-2, when the spur gear of the intermediate double gear set 12 rotates, the spur gear of the intermediate double gear set 12 drives the bevel gear of the intermediate double gear set 12 to rotate in the same direction.

[0095] The continuously variable transmission also includes: an output shaft 13;

[0096] The output shaft 13 is disposed on the central axis of the second clutch bevel gear 11-1 and the second clutch bevel gear 11-1;

[0097] When the rotational speed of the first differential bevel gear 9-3 is equal to the rotational speed of the second differential bevel gear 9-4, the output shaft 13 does not rotate;

[0098] When the rotational speed of the first differential bevel gear 9-3 is greater than the rotational speed of the second differential bevel gear 9-4, the output shaft 13 rotates in the opposite direction.

[0099] When the rotational speed of the first differential bevel gear 9-3 is less than the rotational speed of the second differential bevel gear 9-4, the output shaft 13 rotates in the opposite direction.

[0100] The core principles of this device include: how the two universal joints generate a speed difference, how the generated speed difference is converted into a continuous angular velocity output through the differential 9, and how the output shaft 13 is continuously rotated in one direction through the one-way clutch, and how the entire device achieves a variable speed ratio.

[0101] The two universal joints are the first universal joint 1 and the second universal joint 2.

[0102] The universal joint will generate fluctuating angular velocity. The angular velocity transmitted from the input shaft 5 to the first universal joint 1 and the second universal joint 2 through the synchronous gear is in the same direction and frequency. The two universal joints have a 90-degree phase angle difference, so their output angular velocity curves have a 90-degree phase difference.

[0103] By utilizing the non-uniformity of the output angular velocities of the first universal joint 1 and the second universal joint 2, a differential gear 9 is used to differentiate the output angular velocities of the first universal joint 1 and the second universal joint 2, thereby converting the non-uniform velocity into a continuous output. Figure 5 and Figure 6 As shown, ω1 is a schematic curve showing the change of the output angular velocity of the first universal joint 1 over time, ω2 is a schematic curve showing the change of the angular velocity of the second universal joint 2 over time, and ω3 is a schematic curve showing the change of the angular velocity of the output shaft 13 after passing through the differential 9 over time.

[0104] In this embodiment, the function of the first one-way clutch 10-2 and the second one-way clutch 11-2 is to keep the output shaft 13 of the differential 9 rotating in one direction. Figure 5 and Figure 6 The diagram shows the angular velocity variation of the universal joint with different shaft angles α. As the angular velocity α changes, the angular velocity of the output shaft 13 achieves stepless speed regulation.

[0105] like Figures 1 to 7As shown, the input shaft 5 is fixedly connected to the second synchronous gear 4. The second synchronous gear 4 and the input shaft 5 are connected to the left end of the second universal joint 2 and rotate relative to the movable frame 14. The first synchronous gear 3 is connected to the left end of the first universal joint 1 and rotates relative to the movable frame 14. The intermediate gear 6 rotates relative to the movable frame 14. The first synchronous gear 3 and the second synchronous gear 4 are synchronously transmitted through the intermediate gear 6.

[0106] The right end of the first universal joint 1 is connected to the first bevel gear 8 and rotates relative to the fixed frame 7. The first bevel gear 8 is driven by the second differential bevel gear 9-4, which drives the first drive wheel 9-7 to rotate.

[0107] The right end of the second universal joint 2 is connected to the second bevel gear 15 and rotates relative to the fixed frame 7. The second bevel gear 15 drives the second drive wheel 9-8 to rotate through the first differential bevel gear 9-3.

[0108] The first planetary carrier gear 9-1 and the second planetary carrier gear 9-2 are connected to the differential planetary carrier. The first planetary carrier gear 9-1 transmits power to the first clutch bevel gear 10-1 of the first gear clutch assembly. The first clutch bevel gear 10-1 drives the output shaft 13 to rotate in one direction.

[0109] The second planetary carrier gear 9-2 transmits power to the second clutch bevel gear 11-1 of the second gear clutch assembly via the intermediate double gear set 12. The second clutch bevel gear 11-1 drives the output shaft 13 to rotate in one direction. The output shaft 13 is fixedly connected to the first gear clutch assembly and the second gear clutch assembly.

[0110] The specific principle of continuously variable transmission in this device is as follows:

[0111] Assuming the input shaft 5 rotates in the forward direction, and is connected to the second synchronous gear 4, the first synchronous gear 3 and the second synchronous gear 4 rotate synchronously in the forward direction after being transmitted through the intermediate gear 6. This drives the first universal joint 1 and the second universal joint 2 to rotate. Because there is a 90° phase difference between the first universal joint 1 and the second universal joint 2, the output angular velocity phase difference of the fluctuation velocity generated by the two universal joint assemblies is also 90°. The schematic curve of the output angular velocity of the two universal joint assemblies is shown below. Figure 5 and Figure 6 As shown, ω1 is a schematic curve showing the change of the output angular velocity of the first universal joint 1 over time, and ω2 is a schematic curve showing the change of the angular velocity of the second universal joint 2 over time. Figures 5-6It can be seen that at the same moment, there is a speed difference in the output angular velocity of the two universal joints. Through the transmission of the couplings, the second bevel gear 15 rotates in the same direction as the input shaft 5, and the first bevel gear 8 rotates in the same direction as the first synchronous gear 3, meaning it also rotates in the same direction as the input shaft 5. The second bevel gear 15 transmits the rotation to the first differential bevel gear 9-3, and the rotation direction of the first differential bevel gear 9-3 is as follows... Figure 2 As shown, the first bevel gear 8 drives the second differential bevel gear 9-4 to rotate, and the direction of rotation is as follows. Figure 2 As shown, the first differential bevel gear 9-3 and the second differential bevel gear 9-4 rotate in opposite directions. The second differential bevel gear 9-4 drives the first drive gear 9-7 to rotate, and the first differential bevel gear 9-3 drives the second drive gear 9-8 to rotate. The first drive gear 9-7 and the second drive gear 9-8 simultaneously drive the first planetary gear 9-5 and the second planetary gear 9-6 to rotate. The force on the first planetary gear 9-5 and the second planetary gear 9-6 is related to the rotational speed of the first differential bevel gear 9-3 and the second differential bevel gear 9-4.

[0112] When the rotational speed of the first differential bevel gear 9-3 equals the rotational speed of the second differential bevel gear 9-4, the forces acting on the two planetary gears are equal in magnitude but opposite in direction because the rotation directions are opposite. At this time, the first planetary gear 9-5 and the second planetary gear 9-6 do not "revolve" but only "rotate". At this time, the differential 9 does not swing and the angular velocity of the output shaft 13 is 0.

[0113] When the rotational speeds of the first differential bevel gear 9-3 and the second differential bevel gear 9-4 are different, the difference in their rotational speeds results in different magnitudes of forces acting on the two planetary gears, and the forces are in opposite directions. The difference in the forces causes the planetary gears to revolve. Due to the imbalance of forces, the differential 9 swings at this time.

[0114] like Figure 3 As shown, the swing of differential 9 follows the following principle:

[0115] The rotational speed of the second differential bevel gear 9-4 is greater than that of the first differential bevel gear 9-3. The force transmitted by the first differential bevel gear 9-3 to the two planetary gears is greater than that transmitted by the second differential bevel gear 9-4 to the two planetary gears. This unbalanced force causes the differential 9 (differential planetary carrier) to swing from the inside out in the first direction. The first planetary carrier gear 9-1 rotates under the action of the speed difference between the first differential bevel gear 9-3 and the second differential bevel gear 9-4, and then transmits the power to the first clutch bevel gear 10-1 of the first gear clutch assembly. At this time, the first one-way clutch 10-2 is engaged and the second one-way clutch 11-2 is not engaged, causing the output shaft 13 to rotate in the opposite direction (the input shaft 5 rotates in the forward direction). The forward and reverse directions are used to distinguish the rotation directions of the input shaft 5 and the output shaft 13.

[0116] The rotational speed of the second differential bevel gear 9-4 is less than the rotational speed of the first differential bevel gear 9-3. The force transmitted by the first differential bevel gear 9-3 to the two planetary gears is greater than the force transmitted by the two planetary gears of the second differential bevel gear 9-4. The unbalanced force causes the differential 9 (differential planetary carrier) to swing from the outside to the inside in the second direction. The second planetary carrier gear 9-2 rotates under the action of the unbalanced force. The rotational speed changes according to the magnitude of the force difference and is transmitted to the second clutch bevel gear 11-1 of the second gear clutch assembly through the intermediate double gear set 12. At this time, the second one-way clutch 11-2 is working, the first one-way clutch 10-2 is not working, and the output shaft 13 rotates in the opposite direction.

[0117] In both cases, the output shaft 13 is kept rotating in the same direction by the action of the first one-way clutch 10-2 and the second one-way clutch 11-2.

[0118] The principle by which this structure achieves continuously variable transmission includes:

[0119] The key to achieving the transmission ratio of the entire continuously variable transmission is the included angle α between the two ends of the universal joint. The universal joint is installed at the end of the movable frame 14. When the universal joint rotates, the movable frame 14 will move up and down with the rotation. The reason for the up and down rotation is caused by the structure of the universal joint itself, which is the existing technology.

[0120] Figure 4 This is a schematic diagram of the shaft angle α using the second universal joint 2 as an example. In actual operation, the shaft angle α of the first universal joint 1 and the second universal joint 2 is the same. Since the position of the fixed frame 7, which is slidably connected to the right end of the universal joint assembly, remains unchanged, the change of the shaft angle α is achieved by the up-and-down movement of the movable frame 14.

[0121] When α is 0°, the two ends of the universal joint assembly are on a straight line. At this time, the output angular velocities of the two universal joint assemblies are the same, the differential 9 does not swing, and the speed of the output shaft 13 is 0. The schematic curves of the output angular velocities of the two universal joints and the schematic curve of the output shaft 13 are shown below. Figure 7 As shown; when α is 20°, there is a 90-degree phase difference between the output angular velocities of the two universal joint assemblies. The schematic curves of the output angular velocities of the two universal joints and the schematic curve of the output shaft 13 are shown in the figure. Figure 5 As shown, when α is 35°, the schematic curves of the output angular velocity of the two universal joints and the schematic curve of the output shaft 13 are as follows. Figure 6 As shown. (Through) Figure 5 , Figure 6 , Figure 7 By comparison, it can be seen that the speed of the output shaft 13 changes with the change of the included angle α of the universal joint shaft. In other words, by changing the included angle α of the universal joint assembly, the transmission ratio of the entire continuously variable transmission device can be changed under the transmission principle described above, so that the output shaft 13 achieves stepless speed change in the transmission system of the entire transmission device.

[0122] In another aspect, the present invention provides a method of using a mechanical continuously variable transmission (CVT), applied to the aforementioned mechanical CVT; comprising the following method:

[0123] The input shaft 5 is driven to rotate in the forward direction, and the input shaft 5 drives the second synchronous gear 4 to rotate in the same direction. The second synchronous gear 4 drives the first synchronous gear 3 to rotate in the forward direction through the intermediate gear 6.

[0124] The first synchronous gear 3 drives the first universal joint 1 to rotate in the forward direction, and the second synchronous gear 4 drives the second universal joint 2 to rotate in the forward direction. There is a speed difference between the angular velocity output by the first universal joint 1 and the angular velocity output by the second universal joint 2.

[0125] The first bevel gear 8 drives the second differential bevel gear 9-4 to rotate, and the second bevel gear 15 drives the first differential bevel gear 9-3 to rotate. The first bevel gear 8 and the second bevel gear 15 rotate in the same direction, and the rotation direction of the second differential bevel gear 9-4 is opposite to the rotation direction of the first differential bevel gear 9-3.

[0126] The second differential bevel gear 9-4 drives the first drive wheel 9-7 to rotate, and the first differential 9 drives the second drive wheel 9-8 to rotate. The rotation direction of the first drive wheel 9-7 is opposite to the rotation direction of the drive wheel.

[0127] Specifically, when the rotational speed of the first driving wheel 9-7 is equal to the rotational speed of the second driving wheel 9-8, the output shaft 13 does not rotate;

[0128] Otherwise, output shaft 13 rotates in the opposite direction.

[0129] This device and method generate differential speed solely through rotation, eliminating eccentric inertia and effectively avoiding the technical problems present in existing technologies. This invention innovatively employs a purely mechanical transmission principle, primarily utilizing a combination of two universal joints with a 90° phase difference, a differential, and a one-way gear clutch. The transmission structure is simple, highly efficient, and can meet the demands for flexible speed adjustment, high transmission accuracy, and large reduction ratios. Furthermore, it is easy to manufacture, has low operating and maintenance costs, a small footprint, and can adapt to harsh environments, making it worker-friendly and possessing extremely high application prospects and value.

[0130] The following points need to be explained:

[0131] (1) The accompanying drawings of the embodiments of the present invention only involve the structures involved in the embodiments of the present invention. Other structures can refer to the general design.

[0132] (2) For clarity, the thickness of layers or regions is enlarged or reduced in the drawings used to describe embodiments of the present invention; that is, these drawings are not drawn to actual scale. It is understood that when an element such as a layer, film, region, or substrate is referred to as being “above” or “below” another element, the element may be “directly” located “above” or “below” the other element, or there may be intermediate elements.

[0133] (3) Where there is no conflict, the embodiments of the present invention and the features in the embodiments can be combined with each other to obtain new embodiments.

[0134] The above are merely specific embodiments of the present invention, but the scope of protection of the present invention is not limited thereto. The scope of protection of the present invention should be determined by the scope of the claims.

Claims

1. A mechanical continuously variable transmission, characterized in that, Includes a drive assembly, a first bevel gear, and a second bevel gear; The driving component includes: A movable frame and a fixed frame, wherein the movable frame and the fixed frame are arranged in parallel relative to each other; A first universal joint and a second universal joint are provided. One end of the first universal joint is mounted on the movable frame, and the other end is mounted on the fixed frame. One end of the second universal joint is mounted on the movable frame, and the other end is mounted on the fixed frame. The first universal joint and the second universal joint are arranged with a 90° phase angle difference and are parallel to each other. An input shaft is connected to an end shaft mounted on the movable frame by the second universal joint. The first synchronizing gear is mounted on the end shaft of the first universal joint coupling mounted on the movable frame. A second synchronizing gear is mounted on the input shaft; An intermediate gear is mounted on the movable frame, and a synchronizing gear is disposed between the first synchronizing gear and the second synchronizing gear. The intermediate gear meshes with both the first synchronizing gear and the second synchronizing gear. Wherein, the first bevel gear is installed on the end shaft of the first universal joint mounted on the fixed frame, and the second bevel gear is installed on the end shaft of the second universal joint mounted on the fixed frame; The central axes of the first bevel gear and the second bevel gear are arranged in parallel, and the drive assembly drives the first bevel gear and the second bevel gear to rotate in the same direction.

2. The mechanical continuously variable transmission according to claim 1, characterized in that, It also includes a differential, which comprises: a first planetary gear, a second planetary gear, a first drive gear, a second drive gear, a first planetary carrier gear, a second planetary carrier gear, a differential planetary carrier, a first differential bevel gear, and a second differential bevel gear; The bottom of the first differential bevel gear and the second differential bevel gear mesh, the top of the second differential bevel gear and the first differential bevel gear mesh, the central axis of the first differential bevel gear coincides with the central axis of the second differential bevel gear, the central axis of the second differential bevel gear is perpendicular to the central axis of the second differential bevel gear, and the differential planetary carrier is disposed between the first differential bevel gear and the second differential bevel gear. When the input shaft rotates, the first bevel gear and the second bevel gear rotate in the same direction, while the first differential bevel gear and the second differential bevel gear rotate in opposite directions. Wherein, the first planetary carrier gear is mounted on the differential planetary carrier and is arranged on the same side as the first differential bevel gear, the first bevel gear is connected to the first drive wheel, and the first bevel gear drives the first drive wheel to rotate in the same direction; The second planetary carrier gear is mounted on the differential planetary carrier and is located on the same side as the second differential bevel gear; the second bevel gear is connected to the second drive wheel, and the second bevel gear drives the second drive wheel to rotate in the same direction. The first planetary gear, the second planetary gear, the first drive gear, and the second drive gear are installed in the differential planetary carrier. One side of the first planetary gear meshes with one side of the first driving gear, and the other side of the first planetary gear meshes with one side of the second driving gear; One side of the second planetary gear meshes with the other side of the first driving gear, and the other side of the second planetary gear meshes with the other side of the second driving gear; The second differential bevel gear is connected to the first drive gear via a first connector, and the first connector passes through the first planetary carrier gear; The first differential bevel gear is connected to the second drive gear via a second connector, and the second connector passes through the second planetary carrier gear; Wherein, the first connector and the second connector are on the same axis; When the input shaft rotates in the forward direction, the first universal joint and the second universal joint output angular velocities with a speed difference. The first universal joint drives the first bevel gear to rotate in the forward direction, and the second universal joint drives the second bevel gear to rotate in the forward direction. The first differential bevel gear and the second differential bevel gear rotate in opposite directions. When the rotational speed of the first differential bevel gear is equal to the rotational speed of the second differential bevel gear, the first planetary gear and the second planetary gear output forces of equal magnitude and opposite direction. When the rotational speed of the second differential bevel gear is greater than the rotational speed of the first differential bevel gear, the differential planetary carrier rotates in the first direction around the first connecting member and the second connecting member; When the rotational speed of the second differential bevel gear is less than the rotational speed of the first differential bevel gear, the differential planetary carrier rotates in the second direction around the first connecting member and the second connecting member.

3. The mechanical continuously variable transmission according to claim 2, characterized in that, The continuously variable transmission further includes: a first gear clutch assembly, a second gear clutch assembly, and an intermediate double gear set; The first gear clutch assembly includes: a first clutch bevel gear and a first one-way clutch; The first one-way clutch is mounted on the first clutch bevel gear, and the first clutch bevel gear supports meshing with the first planetary carrier gear. The second gear clutch assembly includes: a second clutch bevel gear and a second one-way clutch; The second one-way clutch is mounted on the second clutch bevel gear. The first clutch bevel gear supports meshing with the bevel gear of the intermediate double gear set. The spur gear of the intermediate double gear set meshes with the second planetary carrier gear. When the spur gear of the intermediate double gear set rotates, the spur gear of the intermediate double gear set drives the bevel gear of the intermediate double gear set to rotate in the same direction.

4. The mechanical continuously variable transmission according to claim 3, characterized in that, The continuously variable transmission further includes: an output shaft; The output shaft is disposed on the central axis of the first clutch bevel gear and the second clutch bevel gear; When the rotational speed of the first differential bevel gear is equal to the rotational speed of the second differential bevel gear, the output shaft does not rotate; When the rotational speed of the first differential bevel gear is greater than the rotational speed of the second differential bevel gear, the output shaft rotates in the opposite direction; When the rotational speed of the first differential bevel gear is less than the rotational speed of the second differential bevel gear, the output shaft rotates in the opposite direction.

5. A method of using a mechanical continuously variable transmission, characterized in that, Applied to the mechanical continuously variable transmission of claim 4; comprising the following method: The input shaft is driven to rotate in the forward direction, and the input shaft drives the second synchronous gear to rotate in the same direction. The second synchronous gear drives the first synchronous gear to rotate in the forward direction through the intermediate gear. The first synchronous gear drives the first universal joint to rotate in the forward direction, and the second synchronous gear drives the second universal joint to rotate in the forward direction. There is a speed difference between the angular velocity output by the first universal joint and the angular velocity output by the second universal joint. The first bevel gear drives the second differential bevel gear to rotate, and the second bevel gear drives the first differential bevel gear to rotate. The first bevel gear and the second bevel gear rotate in the same direction, and the rotation direction of the second differential bevel gear is opposite to that of the first differential bevel gear. The second differential bevel gear drives the first drive wheel to rotate, and the first differential drives the second drive wheel to rotate. The rotation direction of the first drive wheel is opposite to the rotation direction of the second drive wheel. Specifically, when the rotational speed of the first driving wheel is equal to the rotational speed of the second driving wheel, the output shaft does not rotate; Otherwise, the output shaft will rotate in the opposite direction.

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