Ratchet chain type continuously variable transmission

Abstract

This invention belongs to the field of continuously variable transmission (CVT) technology, specifically disclosing a ratchet chain CVT device. It includes a power source, a hydraulic pump, a drive pulley, a driven pulley, and a transmission belt. The power source is axially connected to the drive pulley, providing power. Both the drive pulley and the driven pulley have several pawls arranged circumferentially. The inner wall of the transmission belt is provided with ratchet teeth. A radius adjustment device is also provided on the main shaft of the drive pulley and the driven pulley. The output end of the hydraulic pump is axially connected to the radius adjustment device, used to drive the radius adjustment device. During the speed change process, the transmission of this invention not only increases the output torque but also allows the excess chain released by the drive pulley or driven pulley due to the decrease in radius to be displaced with minimal friction onto the driven or main sprocket, which requires additional chain length due to the increase in radius, thus avoiding wear on the transmission belt.

Description

Technical Field

[0001] This invention belongs to the field of continuously variable transmission (CVT) technology, and specifically relates to a ratchet chain CVT device. Background Technology

[0002] Currently, continuously variable transmissions (CVTs) primarily use steel belt CVTs, which offer advantages such as high energy efficiency and no noticeable shift shock. However, a significant drawback is their insufficient torque, high cost, and susceptibility to wear on the metal belt. This has hindered the widespread adoption and development of steel belt CVTs. We know that steel belt CVTs work by altering the radius of the contact area between the metal belt and the two conical pulleys. For example, increasing the radius of the contact area between the main conical pulley and the steel belt, while decreasing the radius of the contact area between the steel belt and the contact area between the main conical pulley and the main conical pulley, or decreasing the radius of the contact area between the steel belt and the contact area between the main conical pulley and the main conical pulley, while increasing the radius of the contact area between the steel belt and the contact area between the main conical pulley and the main conical pulley. The radius of the contact area between the metal belt and the main conical pulley determines the output speed of the transmission. Of course, changing the radius of the contact area between the metal belt and the main conical pulley also changes the distance between the contact arc of the metal belt and the conical surface. Suppose that on the pulley, the radius of the metal belt and its contact surface with the shaft decreases, then the length of the arc-shaped contact area between the metal belt and this conical surface also decreases, releasing a certain length of metal belt. Simultaneously, on the main pulley, because the radius of the metal belt and its contact surface with the shaft increases, the length of the arc-shaped contact area also increases, requiring the inclusion of the section of metal belt released from the pulley. However, in a steel belt CVT, the metal belt and its contact surface with the pulley rotate asynchronously, resulting in a slippage process along the pulley's contact surface. This means that in a steel belt CVT, the metal belt and pulley must go through a slippage process to complete the gear shift. This involves a crucial core issue: the problem of "friction force." For a steel belt CVT, the gear shifting process itself is a process of the metal belt slipping along the conical surface. The goal is to minimize friction, reducing wear on the steel belt from the conical pulley and minimizing kinetic energy loss. However, during power transmission, it's crucial to maximize static friction; without sufficient static friction, the required torque transmission cannot be achieved. Therefore, in a steel belt CVT, "speed change" and "power transmission" are inherently contradictory, and even the highest quality metal belt is merely a temporary fix.

[0003] Therefore, providing a new ratchet chain continuously variable transmission device is a technical problem that urgently needs to be solved by those skilled in the art. Summary of the Invention

[0004] The purpose of this invention is to overcome the defects in the prior art and provide a ratchet chain continuously variable transmission device.

[0005] This invention provides a ratchet chain continuously variable transmission (CVT). It includes a power source 1, a hydraulic pump 2, a drive pulley 14, a driven pulley 15, and a transmission belt 4. The power source 1 is axially connected to the drive pulley 14, providing power to it. The drive pulley 14 and driven pulley 15 have essentially the same structure, comprising a main shaft and wheel assembly, a branch ratchet chain assembly, and a pyramidal structure. Both the drive pulley 14 and driven pulley 15 have a plurality of pawls 16 arranged circumferentially. The inner wall of the transmission belt is provided with ratchet teeth, and at least one pawl 16 of the drive pulley 14 and driven pulley 15 engages with these ratchet teeth. The main shaft also has a radius adjustment device (pyramid). The output end of the hydraulic pump 2 is connected to the radius adjustment device (pyramid) via a bearing, used to control the radius adjustment device (pyramid).

[0006] A further embodiment includes a main shaft and wheel assembly comprising an axle 3 and two wheel discs 11; the two wheel discs 11 are identical in size and shape; at the center of each wheel disc 11 is a shaft hole that matches the cross-section of the axle 3; strip-shaped holes 13 are arranged on each wheel disc 11, with an included angle of 60 degrees between adjacent strip-shaped holes 13, and the distance from each strip-shaped hole 13 to the center of the wheel disc is equal to the radius of the wheel attached to the axle 3; the two wheel discs 11 are inserted into the axle from both ends of the axle 3, with the surfaces of the two wheel discs 11 parallel and perpendicular to the axle 3; the wheel attached to the axle 3 is sandwiched in the middle. A further embodiment includes pairs of strip-shaped holes 13 on the two wheel discs 11 located at the same angle to the axle 3. A further embodiment includes concave arc grooves on both sides of the strip-shaped holes 13. A further embodiment is that both the driving wheel 14 and the driven wheel 15 are circumferentially provided with several branch ratchet sprocket assemblies; each branch ratchet sprocket assembly includes two sliding blocks 9 and one branch ratchet sprocket 5; the axes of the two sliding blocks 9 and the branch ratchet sprocket 5 are perpendicular and parallel to each other, and the distance between the two sliding blocks 9 is the distance between the two discs 11 on the disc assembly. Each sliding block 9 is formed by two sliding blocks connected by a spring; the two sides of the sliding block 9 are provided with convex arc edges that match the concave arc grooves on the two sides of the strip hole 13. Each branch ratchet sprocket 5 has its two end shafts inserted into a pair of corresponding slotted holes 13 via a pair of sliding blocks 9. The branch ratchet sprocket 5 is positioned between two discs 11, with its two end shafts respectively located in a pair of corresponding slotted holes 13. The shafts of the branch ratchet sprocket 5 and the main shaft are parallel to the wheel axle 3 on the disc assembly, allowing the sliding blocks 9 to carry the branch ratchet sprocket 5 back and forth along the track of the slotted holes 13. In each slotted hole 13, two sliding blocks 9 are connected to the same branch ratchet sprocket 5. Each sliding block 9 has a recessed trapezoidal groove at its end near the wheel axle 3, with the upper base of the trapezoid at the end of the sliding block 9 near the wheel axle 3. Furthermore, the lengths of the two sliding blocks 9 mounted on the same branch ratchet sprocket 5 are not the same. The line connecting the grooves of each pair of sliding blocks 9 forms an angle with the axial direction. The pawl 16 is mounted on the branch ratchet sprocket 5. The drive wheel 14 is provided with a ratchet sprocket 5 and the driven wheel 15 is provided with a ratchet sprocket 5. The ratchet 16s on the drive wheel 14 and the driven wheel 15 are provided with ratchet sprockets ... are slightly pointing in different directions. The ratchet 16s are located at different positions on the axis.

[0007] A further embodiment is that the transmission belt 4 includes three ratchet chains 5 and two triangular belts 19. For the ratchet chains in this invention: for example, on the outer ring of a bicycle freewheel, the ratchet teeth are arranged in a uniform direction on the inner circumference of the freewheel ring. In this invention, the ratchet chain 12 is equivalent to splitting each ratchet segment of this arrangement on the bicycle freewheel ring, linking them together in a chain-like manner to form a loop with a variable arrangement shape. We call this "ratchet chain 12". The three ratchet chains 12 have the same number of ratchet segments. The ratchet arrangement direction of the two ratchet chains 12 on the secondary side of the transmission belt is opposite to that of the ratchet chain 12 in the middle of the transmission belt. The two triangular belts 19 are used to connect the three ratchet chains 12. The three ratchet chains 12 and the two triangular belts 19 are connected by pins 17. A further embodiment is that the branch ratchet sprocket 5 is provided with 6 units. A further embodiment is that the radius adjustment device pyramid comprises a flange, 6 right-angled triangular steel blocks 6, and a section of steel pipe 10; the inner diameter of the flange's central hole and the outer diameter of the steel pipe 10 are equal, both fitted onto the axle 3, and can slide back and forth relative to the axle 3; each section of the hypotenuse of the right-angled triangular steel block 6 has a protruding trapezoidal shape, with the hypotenuse face being the lower base of the trapezoid. The right-angled triangular steel blocks 6 are distributed and fixed on one surface of the flange, with the shorter right-angled side of each block connected to the flange surface, its right angle close to the flange center; the intersection of its left and right sides is close to the flange circumference. Furthermore, the faces of each right-angled triangular steel block 6 are perpendicular to the flange surface. The steel pipe 10 is vertically fixed to the central hole on the other side of the flange, serving as a handle for controlling the radius adjustment device pyramid. The pyramid is inserted into each right-angled triangular steel block 6 in each strip space. The angle of the hypotenuse of each right-angled triangular steel block 6 coincides with the angle formed by the line connecting the grooves of each pair of sliding blocks 9 and the axial direction; these angles are complementary. Simultaneously, the recessed trapezoidal grooves on the sliding blocks 9 also match the protruding trapezoidal cross-sections on the hypotenuse of the pyramid. Therefore, each protruding trapezoidal cross-section of the hypotenuse of the pyramid can be inserted into the trapezoidal recessed groove of its corresponding pair of sliding blocks.

[0008] A further embodiment is that the steel pipe 10 is connected to the output shaft of the hydraulic pump 2 via a bearing 7 and a rod 8, with the hydraulic pump 2 fixed above and below the rod 8.

[0009] Compared with the prior art, the beneficial effects of the present invention are as follows:

[0010] (1) During the speed change process, the transmission of the present invention not only increases the output torque, but also allows the excess transmission belt 4 released by the driving wheel 14 or driven wheel 15 due to the decrease in radius distance to be displaced with minimal friction to the driven wheel 15 or driving wheel 14, which requires an increase in the length of the supplementary transmission belt 4 due to the increase in radius, thereby avoiding wear on the transmission belt 4.

[0011] (2) In this invention, several identical branch ratchet sprockets 5 are evenly distributed on the circumference of the driving wheel 14 and the driven wheel 15, forming a non-continuous, intermittently arranged transmission belt groove segment. This segment is evenly distributed on the circumference of the driving wheel 14 and the driven wheel 15, thus replacing the continuous, integral circumferential transmission belt groove on the driving wheel 14 and the driven wheel 15. It also achieves the same function of supporting, bearing, and fixing the running trajectory of the transmission belt 4.

[0012] (3) The present invention achieves a speed-changing effect by inversely changing the radius distance between the branch ratchet sprockets 5 on the driven wheel 15 and the axle 3 of the driven wheel 14 and the driven wheel 15, respectively, through a novel method.

[0013] (4) In this invention, a ratchet chain 12 is used instead of a metal belt. The ratchet chain 12 engages with the pawls 16 on the drive wheel 14 and the driven wheel 15 respectively, thereby transferring the power from the drive wheel 14 to the driven wheel 15 via the conveyor belt 4. This increases the output torque of the transmission and eliminates static friction between the transmission belt and the pulley. Attached Figure Description

[0014] The following figures are for illustrative purposes only and are not intended to limit the scope of the invention, wherein:

[0015] Figure 1 Schematic diagram of the interaction between the driving / driven pulley and the transmission belt;

[0016] Figure 2 :for Figure 1 Enlarged view of the dotted line area;

[0017] Figure 3 Schematic diagram of the main shaft and wheel assembly structure;

[0018] Figure 4 Schematic diagram of the drive wheel structure;

[0019] Figure 5 Front view of the drive wheel structure;

[0020] Figure 6 A cross-sectional diagram illustrating the principle of inversely proportional change in the radius distance between the driving and driven wheels.

[0021] In the diagram: 1 Power source, 2 Hydraulic pump, 3 Axle (also the drive wheel; or the main shaft of the driven wheel), 4 Transmission belt, 5 Branch ratchet sprocket, 6 Right-angled triangular steel block, 7 Bearing, 8 Rod, 9 Sliding block, 10 Steel pipe, 11 Wheel disc, 12 Racket chain, 13 Strip hole, 14 Drive wheel, 15 Driven wheel, 16 Pawl, 17 Pin, 18 V-belt groove, 19 V-belt. Detailed Implementation

[0022] Detailed Description of Embodiments To make the objectives, technical solutions, design methods, and advantages of the present invention clearer, the present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments. It should be understood that the specific embodiments described herein are only for explaining the present invention and are not intended to limit the present invention.

[0023] like Figure 1 --As shown in Figure 6. This invention provides a ratchet chain continuously variable transmission (CVT). Basic structure: It consists of a power source 1, a driving pulley 14, a driven pulley 15, a transmission belt 4, a device for inversely proportionally changing the radius distance between the driving pulley 14 and the driven pulley 15 (including a hydraulic pump 2), and a device for adjusting the tension of the transmission belt 4, all mounted on a frame assembly.

[0024] Basic Principle: In this invention, the power source 1 and the driving wheel 14 are still axially connected to provide power to the driving wheel 14. The driving wheel 14 pulls the driven wheel 15 through the transmission belt 4. The driving wheel 14 still transmits kinetic energy to the driven wheel 15 through the transmission belt 4. Usually, a complete circular transmission belt groove is provided on the circumference of both the driving wheel 14 and the driven wheel 15 to fix and support the running trajectory of the transmission belt 4. However, in this invention, several branch ratchet sprockets 5 are evenly distributed on the circumference of both the driving wheel 14 and the driven wheel 15, and each branch ratchet sprocket 5 does not have a transmission belt groove. This forms a non-continuous, intermittent arrangement of several scattered transmission belt groove segments, evenly distributed on the circumference of the driving wheel 14 and the driven wheel 15, which can replace the transmission belt grooves that are arranged continuously on the circumference of the driving wheel 14 and the driven wheel 15 (see...). Figure 1 It can also support, carry, and fix the running trajectory of conveyor belt 4.

[0025] The invention also includes a slider track (i.e., a strip-shaped hole 13) provided radially on each branch ratchet sprocket 5 on the drive wheel 14 and driven wheel 15. Each of these branch ratchet sprockets 5 passes through a sliding block 9 and is inserted into its corresponding slider track, allowing the slider to carry these scattered segments back and forth along the grooved track.

[0026] On the driving wheel 14 or driven wheel 15, the radius of the driving wheel 14 or driven wheel 15 is contracted by the movement of each sliding block 9 towards the center of the axle. The radius of the driving wheel 14 or driven wheel 15 is expanded by the simultaneous movement of each sliding block 9 in the opposite direction to the center of the axle. By simultaneously shortening or expanding the distance between each sliding block 9 and the center of the axle on the driving wheel 14, and simultaneously expanding or shortening the distance between each sliding block 9 and the center of the axle on the driven wheel 15, the radius of the driven wheel 14 and driven wheel 15 changes in an inverse proportion, thus achieving a speed-changing effect. Furthermore, pawls 16 are provided on each section of the transmission belt groove of the drive pulley 14 and driven pulley 15, and ratchet teeth are provided on the inner wall of the transmission belt 4. The ratchet chain 12 on the transmission belt 4 engages with the pawls 16 on both the drive pulley 14 and driven pulley 15, thus transferring the power from the drive pulley 14 to the driven pulley 15 via the transmission belt 4. This improves the output torque of the transmission. Simultaneously, during gear shifting, the excess transmission belt 4 released by the reduced radius of the drive pulley 14 or driven pulley 15 can be displaced with minimal friction onto the driven pulley or drive pulley, where the radius increases and additional transmission belt 4 is required. This avoids direct friction between the localized transmission belt 4 and the transmission belt groove during displacement, thereby extending the service life of the transmission belt 4. Technically, this invention can be divided into three working principles.

[0027] The first principle is the principle of changing the radius of the driving wheel 14 and the driven wheel 15; and the second principle is the principle of changing the radius distance between the driving wheel 14 and the driven wheel 15 inversely proportionally.

[0028] In this invention, the driving wheel 14 and the driven wheel 15 have the same basic structure (see reference). Figure 4 The principle of radius change is the same. Each is composed of: a) a main shaft and wheel assembly, b) a 6-branch ratchet sprocket assembly, and c) a pyramid, which are three types of components combined together.

[0029] a: A main shaft and wheel assembly; the main shaft and wheel assembly includes a wheel axle 3 and two wheel discs 11; the two wheel discs 11 are identical in size and shape; at the center of each wheel disc 11, there is a shaft hole that matches the cross-section of the wheel axle 3; strip-shaped holes 13 are arranged on the wheel discs 11, with an included angle of 60 degrees between adjacent strip-shaped holes 13, and the length of each strip-shaped hole 13 from the center of the wheel disc is equal to the radius of the wheel attached to the wheel axle 3; the two wheel discs 11 are inserted into the axle from both ends of the wheel axle 3, the surfaces of the two wheel discs 11 are parallel and perpendicular to the wheel axle 3; the wheel attached to the wheel axle 3 is sandwiched in the middle. (See also) Figure 3A further embodiment is that the six pairs of strip holes 13 on the two discs 11 are each located at the same angle on the axle 3. A further embodiment is that each strip hole 13 has concave arc grooves on both sides. This forms six pairs of strip holes 13, with each pair of strip holes 13 forming a set of slider tracks.

[0030] b: Branched ratchet sprocket assembly: (see...) Figure 2 The branch ratchet sprocket assembly (left and right ends) includes two sliding blocks 9 and one branch ratchet sprocket 5. The branch ratchet sprocket 5 has a transmission belt groove and a pawl 16. The axes of the two sliding blocks 9 and the branch ratchet sprocket 5 are perpendicular and parallel to each other. The distance between the two sliding blocks 9 is the spacing between the two discs 11 on the disc assembly. The two sides of each sliding block 9 have convex arc edges, which match the concave arc grooves on the edges of the strip holes on the wheel axle 3 and disc 11 assembly. Each of the six branch ratchet sprockets 5 passes through its own pair of sliding blocks 9 and is inserted into a corresponding set of strip holes 13 on the main shaft and disc assembly. Each branch ratchet sprocket 5 is located between two discs 11. The shafts at both ends of each branch ratchet sprocket 5 are respectively located in a set of corresponding strip holes 13. The small shaft and wheel axle of each branch ratchet sprocket 5 are parallel to the wheel axle 3 on the disc assembly. Each pair of sliding blocks 9 can carry the branch ratchet sprocket 5 back and forth along the track of the strip holes 13.

[0031] c: Pyramid: A pyramid is made up of three components.

[0032] c1: 6 right-angled triangular steel blocks 6 that are identical in size and shape. On each section of the hypotenuse of each steel block, there is a protrusion of the same trapezoidal shape, and the hypotenuse face is the lower base of the trapezoid.

[0033] c2: A section of steel pipe 10.

[0034] c3: A flange. The distance between the center holes of the flange is equal to the distance between the outer diameters of the steel pipe 10, and the distance between the inner diameters of the steel pipe 10 is slightly larger than the diameter of the axle 3 of the main shaft wheel. According to the angular positions of the 6 sets of strip holes, these 6 right-angled triangular steel blocks 6 are distributed and fixed on one face of the flange. The shorter right-angled side is connected to the flange face; its right angle is close to the center of the flange; the intersection point of its left and right sides with the shorter right-angled side is close to the circumference of the flange. Furthermore, the faces of each right-angled triangular steel block 6 are perpendicular to the flange face. On the other face of the flange, the steel pipe 10 is vertically fixed to this center hole. After this assembly is completed, this section of steel pipe 10 is equivalent to the handle of a pyramid. The handle of the pyramid (steel pipe 10) is fitted onto one end of the axle 3 of the main shaft and wheel assembly, and these 6 right-angled triangular steel blocks are simultaneously inserted into the 6 sets of strip holes 13. The long right-angled side touches the end of the slot 13 closest to the axle 3, the short right-angled side is parallel to the slot 13, the long right-angled side is perpendicular to the slot 13, and the hypotenuse is related to the sliding block 9. Now examine how the pair of sliding blocks 9 on the same branch ratchet sprocket assembly in each set of slots 13 on the two discs 11 are related to the hypotenuse of the corresponding right-angled triangular steel block 6 on the pyramid.

[0035] (a): In each set of strip-shaped holes 13, two sliding blocks 9 are connected to the same branch ratchet sprocket 5. Each sliding block 9 has a recessed trapezoidal groove at the end near the center of the wheel axle 3, with the upper base of the trapezoid located at the end of the slider near the center of the main axis. Furthermore, the lengths of each set of sliding blocks 9 are different, and the line connecting the grooves of each set of sliding blocks forms an angle with the axial direction. (See...) Figure 2 )

[0036] (b): The angle of the hypotenuse of the right-angled triangular steel block 6 inserted into each of the strip holes 13 is also coincidentally complementary to the angle formed by the line connecting the grooves of each set of sliding blocks 9 and the axial direction. (See also) Figure 6 )

[0037] (c): At the same time, the recessed trapezoidal groove on the sliding block 9 also matches the protruding trapezoidal cross-sections on the hypotenuse of the pyramid. (See also) Figure 5 Therefore, each right-angled triangular steel block 6 on the pyramid has its hypotenuse protruding from the trapezoidal cross section, which can be inserted into the trapezoidal recess of its corresponding set of sliding blocks 9.

[0038] The principle of diameter change for driving wheel 14 and driven wheel 15:

[0039] On the driving wheel 14 and driven wheel 15, both ends of the axle 3 are fixed to the frame via bearings 7, and the position of the axle 3 remains unchanged. It should be noted that on the driving wheel 14 and driven wheel 15, each branch ratchet sprocket assembly reciprocates along the radial direction of the slots 13 on the two discs 11, while the pyramid reciprocates along the axis of the axle 3. We change the distance of the pyramid entering and exiting each slot 13 by the reciprocating displacement of the pyramid handle along the axis of the axle 3. Alternatively, the distance occupied by the right-angled triangular steel block 6 in each slot 13 can change, causing the sliding block 9 within the slot 13 to slide along the slot, thus changing the radius of each branch ratchet sprocket 5 from the axle 3. (See...) Figure 5 In the slot 13, when the distance from the radius of the trapezoidal cross-section on the hypotenuse of each right-angled triangular steel block 6 of the pyramid to the center radius of the axle 3 increases, the lower base of the trapezoidal cross-section on the hypotenuse of each right-angled triangular steel block 6 of the pyramid, through the sliding block 9, pushes the radius of each branch ratchet sprocket 5 to increase. When the distance from the radius of the trapezoidal cross-section on each side of the pyramid to the center radius of the axle decreases, the two waist surfaces of the trapezoidal cross-section on the hypotenuse of each right-angled triangular steel block 6 of the pyramid, through the sliding block 9, pull the radius of each branch ratchet sprocket 5 to decrease. This is the principle of radius change for the driven wheel 15 and the driving wheel 14.

[0040] The principle of inverse proportional diameter change between driving wheel 14 and driven wheel 15 (see...) Figure 6 ): Figure 6 This is a top-view cross-sectional diagram illustrating the principle of inverse proportional change in the radii of the driving and driven wheels. The top and bottom directions in this diagram essentially represent the front and rear directions, or inward and outward directions, of this transmission. This is for illustrative purposes only.

[0041] Firstly, the driving wheel 14 and driven wheel 15 are each fixed to the support body at both ends of their axles 3 via bearings 7. These two pyramids are positioned side-by-side at the same horizontal level. Hydraulic pumps 2 are fixed above and below the support body in this diagram, sharing the same output shaft. The handles of each pyramid pass through a bearing 7; a section of rod 8 connects to the output shaft of the hydraulic pump 2, uniting the two pyramids as one. The inner sleeve of the bearing 7 connects to the pyramid handle, and the outer sleeve connects to the rod 8. When the upper hydraulic pump 2 operates, it applies a downward force to the output shaft, causing the two pyramids to move downwards synchronously. When the lower hydraulic pump 2 operates, it applies an upward force to the output shaft, causing the two pyramids to move upwards synchronously. The function of the bearing 7 is to apply only an upward or downward force to the pyramids, without interfering with the pyramids' rotation with the driving wheel 14 or driven wheel 15. Because the handle of the pyramid on the driving wheel faces downwards, while on the driven wheel, the handle faces upwards. When the upper hydraulic pump 2 generates force, the right-angled triangular steel blocks 6 on the pyramid of the driven wheel 15 gradually increase their space occupied in the slot 13. Consequently, the distance between each branch ratchet sprocket 5 on the driven wheel 15 and the axle 3 gradually increases, thus gradually increasing the radius of the driven wheel 15. Simultaneously, the right-angled triangular steel blocks 6 on the pyramid of the driving wheel 14 gradually decrease their space occupied in the slot 13. Consequently, the distance between each branch ratchet sprocket 5 on the driving wheel 14 and the axle 3 gradually decreases, thus gradually shortening the radius of the driving wheel 14. When the lower hydraulic pump 2 generates force, the right-angled triangular steel blocks 6 on the pyramid of the driven wheel 15 gradually shorten their space occupied in the slot 13, thus gradually shortening the radius of the driven wheel 15. Simultaneously, the right-angled triangular steel blocks 6 on the pyramid of the driving wheel 14 gradually increase their spatial position within the slot 13, and the radius of the driving wheel 14 gradually increases. Because the driving wheel 14 and the driven wheel 15 are at the same horizontal spatial position, and the angles of the right-angled triangular steel blocks 6 on both pyramids are the same, when both pyramids are at half the position of the slot 13, the radii of the driving wheel 14 and the driven wheel 15 are equal under this condition. Therefore, regardless of whether the two pyramids are displaced upwards or downwards, the radii produced by the driving wheel 14 and the driven wheel 15 are always inversely proportional. For example, on the driving wheel 14, for every unit S distance the pyramid moves upwards beyond the slot, the radius of the driving wheel 14 increases by a unit r. Simultaneously, for every unit S distance the pyramid on the driven wheel 15 moves upwards beyond the slot, the radius of the driven wheel 15 decreases by a unit r. That is, when the radius of the driving wheel 14 is at its maximum, the radius of the driven wheel 15 is at its minimum, and when the radius of the driving wheel 14 is at its minimum, the radius of the driven wheel 15 is at its maximum. This also explains that the conveyor belt released by the driving wheel 14 and the driven wheel 15 due to a certain reduction in radius is basically equal to the length of the conveyor belt required to increase that distance due to a certain increase in radius.

[0042] Secondly, the basic principle of ratchet chain 12 transmission; and during gear shifting, the excess transmission belt 4 released by the driving pulley 14 or driven pulley 15 due to the decrease in radius is displaced with minimal friction onto the driven pulley 15 or driving pulley 14, which requires additional transmission belt 4 due to the increase in radius. This avoids direct friction between the local transmission belt 4 and the transmission belt groove during displacement, thus extending the service life of the transmission belt.

[0043] As mentioned earlier, this invention is similar to a steel belt continuously variable transmission (CVT), where the drive pulley 14 pulls the driven pulley 15 via the transmission belt 4. However, this invention features several identical branched ratchet sprockets 5 evenly distributed around the circumferences of both the drive pulley 14 and the driven pulley 15. This forms a discontinuous, intermittent arrangement of several transmission belt groove segments that can accommodate the transmission belt 4, evenly distributed around the circumferences of the drive and driven pulleys. This replaces the continuous, circumferential arrangement of the transmission belt grooves on the drive and driven pulleys 14 and 15. The transmission belt 4 of this invention is placed within these segments of the transmission belt grooves on the drive and driven pulleys 14 and 15. This also achieves the functions of supporting, bearing, and fixing the running trajectory of the transmission belt. Compared to a steel belt CVT, this invention also features a ratchet chain 12 on the transmission belt 4, replacing the metal belt. Meanwhile, in this invention, pawls 16 are installed in the transmission belt grooves of each segment on the driving pulley 14 and the driven pulley 15. The ratchet chain 12 engages with the pawls 16 on the driving pulley 14 and the driven pulley 15 respectively, thus transferring the power from the driving pulley 14 to the driven pulley 15 via the conveyor belt 4. The key technology that improves the output torque of the transmission in this invention is the principle that the ratchet chain 12 on the transmission belt 4 can engage with the pawls 16 on the driving pulley 14 and the driven pulley 15 respectively. Other technologies in this invention revolve around the transmission technology of the ratchet chain 12. Before introducing the basic transmission principle of the ratchet chain 12, let's understand the structural form of the ratchet chain 12.

[0044] To illustrate, consider the ratchet teeth on the outer ring of a bicycle freewheel. These teeth are arranged in a uniform direction on the inner circumference of the freewheel ring. In this invention, the ratchet chain 12 is equivalent to splitting each ratchet segment of the bicycle freewheel ring into a single, uniform arrangement. Similar to a chain, each pair of adjacent ratchet segments is linked by a pin, forming a looping, variable-arrangement ratchet chain, which we call the "ratchet chain 12".

[0045] The purpose of the ratchet chain 12 transmission is as follows: When the power source 1 drives the drive wheel 14 to rotate clockwise, the ratchet chain 12 is driven to rotate clockwise by engaging a pawl 16 on the drive wheel 14 with a tooth on the ratchet chain 12. This clockwise rotation of the ratchet chain 12 also engages a pawl 16 on the driven wheel 15 with a tooth on the ratchet chain 12. This transmits the power from the drive wheel 14 to the driven wheel 15 via the ratchet chain 12, thereby increasing the output torque of the transmission.

[0046] We can consider each ratchet link on the ratchet chain 12 as a right-angled triangle. Of course, each ratchet link completes the engagement by contacting the pawl tip 16 through this short right-angled side. First, power source 1 rotates clockwise. Naturally, the drive wheel 14, ratchet chain 12, and driven wheel 15 also rotate clockwise. Since the drive wheel 14 rotates clockwise, the pawl 16 on the drive wheel 14 must point clockwise, and the short right-angled sides of each ratchet tooth on the ratchet chain 12 must be in their own counter-clockwise direction. Only under these conditions can the pawl 16 on the drive wheel 14 engage with the short right-angled sides of the ratchet chain 12, allowing the drive wheel 14 to drive the ratchet chain 12 to rotate clockwise and apply power to the ratchet chain 12. Now, with the short right-angled sides of each ratchet tooth in their own counter-clockwise direction, can the ratchet chain 12, while rotating clockwise, also drive the driven wheel 15 to rotate clockwise? Think about it! Let's analyze the situation. Under what conditions can the ratchet chain 12, which rotates clockwise, drive the driven wheel 15 to rotate clockwise? Our reasoning reveals that regardless of whether the pawl 16 on the driven wheel 15 points slightly clockwise or counterclockwise, the ratchet chain 12 cannot engage with the pawl 16 on the driven wheel 15. Therefore, the ratchet chain 12 cannot drive the driven wheel 15 to rotate clockwise. Thus, in this configuration, the driving wheel 14 cannot drive the driven wheel 15 to rotate clockwise via the ratchet chain 12.

[0047] However, we can further deduce that if we require the ratchet chain 12 to also drive the driven wheel 15 clockwise when rotating clockwise, then the pawl 16 on the driven wheel 15 must point counterclockwise, and the short right-angled sides of each ratchet tooth on the ratchet chain 12 must be clockwise. Under this configuration, when the ratchet chain rotates clockwise, the ratchet chain 12 can engage with the pawl 16 on the driven wheel 15, allowing the ratchet chain 12 to drive the driven wheel 15 clockwise. Only then can the power from the ratchet chain 12 be applied to the driven wheel 15. Regarding this issue, we first need to clarify that on the driving wheel 14, it is the driving wheel 14 that drives the ratchet chain 12 clockwise. However, on the driven wheel 15, it is the ratchet chain 12 that drives the driven wheel 15 clockwise. In other words, this is under the premise of clockwise rotation. The driving gear 14 and driven gear 15 are matched with two different types of meshing systems, or rather, two different meshing formats. In the driving gear 14 meshing system: its pawl 16 points clockwise; and on this ratchet chain 12, the short right-angled sides of each ratchet tooth are in the counter-clockwise direction. In the driven gear 15 meshing system: its pawl 16 points slightly counter-clockwise; and on this ratchet chain, the short right-angled sides of each ratchet tooth are in the clockwise direction. It can be seen that in the two meshing systems of the driving gear 14 and driven gear 15, the directions of the pawl 16 and the directions of the short right-angled sides of the ratchet teeth on the ratchet chain 12 are completely opposite. This invention combines two opposing meshing systems, the driving wheel 14 and the driven wheel 15. The transmission belt 4 in this invention is formed by combining two ratchet chains 12, each with the same number of ratchet segments and opposite ratchet orientations, that match the driving wheel 14 and the driven wheel 15 into a single transmission belt 4. This transmission belt 4, composed of the two ratchet chains 12, is arranged in the ratchet grooves of the driving wheel 14 and the driven wheel 15 (a ratchet groove is the space on a ratchet sprocket where several ratchet chains are arranged).

[0048] The driving sprocket 14 and the driven sprocket 15 are interconnected. On each cross-section of the ratchet groove of the driving sprocket 14 and the driven sprocket 15, there are two parallel ratchet chain 12 running paths. The pawl 16 on the driving sprocket 14 is positioned in the ratchet groove, corresponding to the running path of the other ratchet chain 12. Similarly, the pawl 16 on the driven sprocket 15 is also positioned in the ratchet groove, corresponding to the running path of the other ratchet chain 12. Because each link of the two ratchet chains 12 is connected together, the power from the driving sprocket 14 can be transmitted to the driven sprocket 15 through these two ratchet chains 12. This is the ratchet chain 12 transmission principle, and also the fundamental principle behind this invention for improving output torque.

[0049] In fact, the design of this transmission not only requires increasing the output torque, but also requires reducing friction between the ratchet chain and the transmission belt grooves during gear shifting. (See also...) Figure 2 ), ( Figure 2 )for( Figure 1 (Enlarged view of the dashed line area)

[0050] ( Figure 2 The middle part is ( Figure 1 The transmission band 4 structure format on ) . (See Figure 2 In this invention, the conveyor belt 4 (middle section) is composed of three ratchet chains 12 with the same number of ratchet segments and two identical triangular belts 19. The two triangular belts 19 are located on opposite sides of each cross-section of the conveyor belt 4; the secondary sides consist of two ratchet chains 12 with their short right-angled ratchet sides rotating counter-clockwise; the middle side consists of a single ratchet chain 12 with its short right-angled ratchet sides rotating clockwise. The trapezoidal upper base of the two triangular belts 19 and the ratchet surfaces of the three ratchet chains 12 are on the same surface of the conveyor belt 4. If the triangular belts 19 and ratchet chains 12 on the conveyor belt are considered to be arranged longitudinally side-by-side, then on each cross-section of the conveyor belt 4, the three ratchet segments are arranged side-by-side on the same horizontal line, connected by a single pin 17. The two ends of the pin 17 are respectively bonded to the lower base of the trapezoidal cross-section of the two triangular belts 19. These pins 17 combine the two triangular belts 19 and the three ratchet chains 12 into a single conveyor belt 4.

[0051] ( Figure 2 The right end indicates: its ( Figure 1 The format of the ratchet sprocket assembly on the drive wheel 14 within the dashed line also shows the format of each ratchet sprocket assembly on the drive wheel 14.

[0052] ( Figure 2 The left end indicates: its ( Figure 1 The format of the ratchet sprocket assembly on the driven wheel 15 within the dashed line also shows the format of each ratchet sprocket assembly on the driven wheel 15.

[0053] Composition of the branched ratchet sprocket 5: (see...) Figure 2 The branch ratchet sprockets 5 on the driving pulley 14 and driven pulley 15 (left and right ends) are basically the same in structure. Each branch ratchet sprocket 5 consists of two pulleys with triangular belt grooves 18, each passing through a bearing 7 and mounted on the two ends of a small pulley shaft. The branch ratchet sprocket 5 essentially supports the transmission belt groove of the transmission belt 4. The transmission belt groove includes the triangular belt groove 18 and the ratchet groove. The pawl 16 is mounted on the small pulley shaft of the ratchet groove.

[0054] On the driving sprocket 14 and driven sprocket 15, the axles at both ends of each branch ratchet sprocket 5 pass through the sliding block 9 and are inserted into their respective slotted holes 13. To use a vivid analogy, the small axles on each branch ratchet sprocket 5 on the driving sprocket 14 and driven sprocket 15 can only revolve around the axle 3 of the driving sprocket 14 or driven sprocket 15, but do not rotate on their own axis. Therefore, the tips of each pawl 16 must be located on the circumference of each branch ratchet sprocket 5, at the position furthest from the center of the axle 3 of the driving sprocket 14 or driven sprocket 15. Instead, the pawls 16 on the small axles of each branch sprocket remain fixed on the circumference of the driving sprocket 14 and driven sprocket 15 (see [reference]). Figure 4 ).

[0055] However, the two pulleys with triangular grooves 18 can not only revolve around the axle 3 of the driving pulley 14 or the driven pulley 15, but also rotate on their own axis as needed.

[0056] (See also) Figure 2 In this transmission, the transmission belt 4 is respectively installed in the transmission belt grooves on the drive pulley 14 and the driven pulley 15. The transmission belt 4 matches the transmission belt grooves on the drive pulley 14 and the driven pulley 15, thus connecting the drive pulley and the driven pulley. The two V-belts 19 on the transmission belt 4 match the V-belt grooves 18 on both sides of the branch ratchet sprockets 5 on the drive pulley 14 and the driven pulley 15, respectively. The three ratchet chains 12 on the transmission belt 4 are respectively located in the ratchet chain grooves on the branch ratchet sprockets 5 on the drive pulley 14 and the driven pulley 15. That is to say, on the drive pulley 14 and the driven pulley 15, the ratchet grooves of each branch ratchet sprocket 5 contain the running trajectory space of the three parallel ratchet chains 12. Therefore, the space occupied by each ratchet groove is divided into three parts corresponding to the three ratchet chains 12.

[0057] The transmission system of this continuously variable transmission (CVT) is essentially composed of two meshing systems: the meshing system of the driving wheel and the meshing system of the driven wheel combined together.

[0058] The drive wheel's meshing system:

[0059] On the drive sprocket 14, the pawls 16 on each branch ratchet sprocket 5 are installed on both sides of their respective ratchet groove cross-sections, with the pawls 16 pointing slightly clockwise. These pawls correspond to and engage with the two ratchet chains 12 on the two sides of the transmission belt 4. Furthermore, on these two ratchet chains 12, the short right-angled sides of each ratchet tooth are in their own counter-clockwise direction, thus enabling them to mesh with the pawls 16 on the drive sprocket 14.

[0060] The driven pulley's meshing system: On the driven pulley 15, the pawls 16 on each branch ratchet sprocket 5 are installed at the center of their respective ratchet groove cross-sections. The pawls 16 point slightly counterclockwise, corresponding to and engaging with the ratchet chain 12 in the middle of the transmission belt 4. On this ratchet chain, the short right-angled sides of each ratchet tooth are in their own clockwise direction. The pawls 16 of the driven pulley 15 match and engage. Because these two meshing systems are combined and linked, the power from the drive pulley 14 can be applied to the driven pulley 15 via the transmission belt 4. In this transmission, the pawls 16 on both the drive pulley 14 and the driven pulley 15 engage with the ratchet chain 12, which obviously improves the transmission torque.

[0061] Why are two identical ratchet chains 12 used in the meshing system of the driven pulley 15? This is because if only one ratchet chain 12 were used in the meshing system of the driving pulley 15, the direction of the connection between the pawls 16 on the driving pulley 14 and the pawls 16 on the driven pulley 15 would not be consistent with the arrangement direction of the transmission belt 4. This would cause wear on the transmission belt 4 and loss of kinetic energy during the operation of the transmission. Therefore, the transmission belt 4 in this invention is composed of three ratchet chains 12 combined together. The force applied from the two pawls 16 on the driving pulley 14 to one pawl 16 on the driven pulley 15 is a resultant force, and the direction of this resultant force is consistent with the direction of the transmission belt 4. This avoids wear on the transmission belt 4 and loss of kinetic energy.

[0062] The functions of the V-belts on both sides of the transmission belt 4 are as follows: 1. During gear shifting, the excess transmission belt 4 released by the driving pulley 14 or driven pulley 15 due to the decrease in radius will shift onto the driven pulley 15 or driving pulley 14, which requires additional transmission belt length due to the increase in radius. This results in the ratchet chain 12 partially crossing the ratchet groove. 2. Because the transmission belt 4 is under tension and is taut, it will generate a force on the ratchet groove pointing in the direction of the wheel axle 3. Without these two V-belts 19, this would undoubtedly increase the frictional force of the ratchet chain 12 crossing the ratchet groove. With two V-belts 19 attached, the three ratchet chains 12 are bound to the two V-belts 19. The force exerted by the three ratchet chains 12 in the direction of the axle 3 is supported by the two V-belts 19. The two V-belts 19 and the two side plates of each branch ratchet sprocket 5 work together to support the three ratchet chains 12 and fix their movement trajectory. This ensures that the three ratchet chains 12 and their corresponding pawls 16 are in contact, but maintain a certain spatial distance from the bottom of the ratchet groove. This avoids friction between the three ratchet chains 12 and the bottom of the ratchet groove when they make local displacement during speed change. The bearings 7 on the two side plates of each branch ratchet sprocket 5 serve to support the three ratchet chains 12 with minimal friction, allowing them to move freely and smoothly in clockwise and counterclockwise directions. The ratchet grooves provide the three ratchet chains 12 with space and a displacement channel.

[0063] The excess conveyor belt 4 released due to the reduced radius of the drive pulley 14 or driven pulley 15 is displaced with minimal friction onto the driven pulley 15 or drive pulley 14, where the radius has increased and additional conveyor belt 4 is required. This is achieved by the ratchet chain on the drive pulley engaging with pawls, and the pawls on the driven pulley engaging with the ratchet chain, each constantly switching and alternating their engagement with the ratchet chain. This allows the power source to be applied from the drive pulley to the driven pulley via the three ratchet chains. During gear shifting, there is a local ratchet chain transfer process, but at each time point and on each pulley, the alternating engagement of pawls with the ratchet chain on the drive and driven pulleys still follows the following rules.

[0064] First, we consider the ratchet chain on the gearbox. For each time period and each pulley's ratchet engagement, the boundary is defined by the two points where the ratchet pawls on the transmission belt engage with the driving and driven pulleys. We divide this ratchet chain into two segments. The transmission belt above these two points is the upper segment. The transmission belt below these two points is the lower segment. Each segment constitutes a separate system. In essence, local ratchet chain displacement can occur through two pathways: one pathway involves disengaging a local ratchet chain while the other incorporates it, resulting in a complementary neutralization.

[0065] During gear shifting, the ratchet chain attached to the driving and driven pulleys constantly contracts or expands in length, centered on the point where it engages with the pawl. When the radius of the driving or driven pulley shortens, the excess ratchet chain released due to the smaller radius splits into two paths, one clockwise and the other counterclockwise, as the point where the belt engages with the pawl on that pulley.

[0066] When the radius of the driving wheel or driven wheel expands, the ratchet chain required to increase the radius is determined by the position where the transmission belt engages with the pawl on the driving wheel or driven wheel. The ratchet chain enters the driving wheel or driven wheel simultaneously in both clockwise and counterclockwise directions from the engaging pawl.

[0067] To illustrate this principle, let's take the example of a transmission where "the radius of the driving pulley decreases while the radius of the driven pulley increases." Due to the restraining effect of the driven pulley on the transmission belt, when the radius of the driving pulley shrinks, it's equivalent to the attached transmission belt on the driving pulley being discharged outwards and collected by the driven pulley onto the upper ratchet chain.

[0068] Based on the arrangement of the pawls and ratchet teeth on the driving wheel, when the radius of the driving wheel contracts, the pawls engaging at this time, rotating counterclockwise, are equivalent to moving clockwise along the ratchet chain. The ratchet chain moving clockwise along the pawls reduces the engagement distance between the pawls and the contacting ratchet teeth. The pawls and ratchet chain tend to engage, but this doesn't mean they are fully engaged. Even when the pawls and ratchet teeth are not fully engaged, although their engagement distance is short and limited, there is still some margin between the pawls and the engagement point. Therefore, within this distance before engagement, the remaining ratchet chain can flow counterclockwise along the pawls into the driven wheel. (As the pawls on the drive wheel engage counterclockwise in this time, the distance between each pawl and the short right-angled side of the ratchet chain they contact decreases. Once a pawl engages with the short right-angled side, it will resist and replace the pawl that engaged in the previous time. This becomes the watershed for the remaining ratchet chain exiting the drive wheel in the next time.)

[0069] When the driven wheel radius expands, it's equivalent to the pawls in the clockwise direction of the current engagement moving clockwise along the ratchet chain, effectively increasing the engagement distance between the pawls and the contacting ratchet teeth. Therefore, the pawls in the clockwise direction of the current engagement can pass over the ratchet chain clockwise, which is equivalent to the ratchet chain flowing into the driven wheel in the counter-clockwise direction on the driving wheel. In the clockwise direction of the pawls, on the lower section of the ratchet chain, based on the arrangement of the pawls and ratchet teeth on the driving wheel, it can be seen that when the driving wheel radius contracts, it's equivalent to the pawls in the clockwise direction of the current engagement moving counter-clockwise along the ratchet chain, effectively increasing the engagement distance between the pawls and the contacting ratchet teeth. Therefore, the ratchet chain in the clockwise direction of the current engagement can compress the springs on each pawl, allowing it to pass over each pawl and exit the driving wheel clockwise.

[0070] On the driven wheel, the pawls engaging counter-clockwise on the current time are equivalent to running counter-clockwise along the ratchet chain. This reduces the engagement distance between the pawl and the contacting ratchet teeth, causing the pawl and ratchet chain to tend to engage, but not necessarily to achieve full engagement. Even when the pawl and ratchet teeth are not fully engaged, although their engagement distance is short and limited, there is still some leeway between the pawl and the engagement point. Therefore, within this distance before engagement, each pawl can pass through the ratchet chain counter-clockwise. This is equivalent to the portion of the ratchet chain displaced clockwise by the driving wheel's pawl engaging clockwise flowing into the driven wheel's pawl's counter-clockwise position. (As the driven wheel rotates counterclockwise, the distance between each pawl and the short right-angled side of the ratchet chain that it contacts decreases. Once a pawl engages with the short right-angled side, it will resist and replace the original engaging pawl, becoming the watershed for the next time the driven wheel accepts the ratchet.)

[0071] The aforementioned localized ratchet chain displacements are all accomplished through the rotation of the ratchet sprockets around the bearings. As previously mentioned, the force applied by the transmission belt is supported by the wheel plates on both sides of each ratchet sprocket, ensuring a certain spatial distance between the ratchet chain and the bottom of its corresponding ratchet groove. This avoids direct friction between the ratchet chain and the bottom of the ratchet groove during localized displacement. (Of course, the frictional force generated between the pawl and the ratchet chain is very limited.) Therefore, it greatly reduces the frictional force generated by these localized ratchet chain movements.

[0072] ① The pawl on the driving wheel engages with the ratchet chain slightly below the driving wheel. The pawl on the driven wheel engages with the ratchet chain slightly above the driven wheel. In this situation, on the upper section of the conveyor belt, the length of the ratchet chain discharged by the driving wheel due to its radius contraction is greater than the length of the ratchet chain that the driven wheel needs to replenish due to its radius expansion. After some of the ratchet chain discharged by the driving wheel due to radius contraction replenishes the driven wheel, the remaining ratchet chain is stored on the upper section of the conveyor belt, becoming slack. On the lower section of the conveyor belt, the length of the ratchet chain discharged by the driving wheel due to radius contraction is less than the length of the ratchet chain that the driven wheel needs to replenish due to its radius expansion. Although the ratchet chain discharged by the driving wheel due to radius contraction also replenishes the driven wheel, it still cannot meet the driven wheel's requirement for the required length of ratchet chain, thus creating tension on the lower section of the conveyor belt. This applies a clockwise traction force directly to the driving wheel and a counterclockwise traction force to the driven wheel.

[0073] Based on the layout of the pawls and ratchet chains on the drive and driven pulleys of the gearbox, it can be inferred that, on the drive pulley, the ratchet chain can pass over the individual ratchet sprockets on the drive pulley in a clockwise direction. On the driven pulley, the ratchet chain can pass over the individual ratchet sprockets on the driven pulley in a counterclockwise direction. Under the tension of the lower transmission belt, the pawls on both the drive and driven pulleys undergo a process of disengaging from the ratchet chain. The remaining transmission belt stored on the upper transmission belt is injected into the following parts of the driven pulley engagement point, simultaneously moving clockwise from the drive pulley and counterclockwise from the driven pulley (effectively accelerating the clockwise speed of the lower transmission belt and slowing down the clockwise speed of the upper transmission belt).

[0074] Simultaneously, the slack in the upper conveyor belt effectively removes the drive pulley from the load. These factors accelerate the clockwise rotation speed of the drive pulley, re-engaging the pawl and the remaining ratchet chain on the upper conveyor belt. The drive pulley then rotates around the bearing, displacing itself into the lower conveyor belt.

[0075] ② The pawl on the driving wheel engages with the ratchet chain slightly above the driving wheel. The pawl on the driven wheel engages with the ratchet chain slightly below the driven wheel. In this situation, on the lower section of the conveyor belt, the length of the ratchet chain discharged by the driving wheel due to its radius contraction is greater than the length of the ratchet chain required to be supplemented by the driven wheel due to its radius expansion. After some of the ratchet chain discharged by the driving wheel due to radius contraction is supplemented by the driven wheel, the remaining ratchet chain is stored on the lower section of the conveyor belt, making the lower section of the conveyor belt slack. However, on the upper section of the conveyor belt, the length of the ratchet chain discharged by the driving wheel due to radius contraction is less than the length of the ratchet chain required to be supplemented by the driven wheel due to its radius expansion. Although the ratchet chain discharged by the driving wheel due to radius contraction is also supplemented by the driven wheel, it still cannot meet the driven wheel's requirement for the length of the ratchet chain, thus creating a tension on the upper section of the conveyor belt. This tension applies a counter-clockwise traction force to the lower conveyor belt via the drive pulley on the right end. This tension applies a clockwise traction force to the lower conveyor belt via the driven pulley on the left end. Based on the layout of the pawls and ratchet chains on the drive and driven pulleys of the gearbox, the ratchet chain on the drive pulley cannot move counter-clockwise past the individual ratchet sprockets on the drive pulley. Similarly, on the driven pulley, the ratchet chain cannot move clockwise past the individual ratchet sprockets on the driven pulley. This tension force on the upper conveyor belt can only increase the engagement of a specific pawl and ratchet chain on the drive and driven pulleys. In other words, a tension is generated on the upper conveyor belt, directly applying a counter-clockwise traction force to the drive pulley and a clockwise traction force to the driven pulley. For the drive pulley, this is a counter-clockwise force. The driven wheel rotates in the opposite direction to the driving wheel, but the tension exerts a clockwise force on it, in the same direction as the driven wheel's movement. Therefore, it affects the driven wheel, increasing its clockwise speed. In general, the excess ratchet chain stored on the lower conveyor belt is moved to the driven wheel in two steps. First, the driven wheel rotates clockwise around its own axis, moving the excess ratchet chain from the lower conveyor belt clockwise over the driven wheel and into the upper conveyor belt. Second, on the driven wheel, a branch ratchet sprocket rotates counter-clockwise around its own axis, moving the remaining ratchet chain from the upper conveyor belt counter-clockwise to the driven wheel. It's worth noting that the tension in the upper conveyor belt directly affects the radius of the driving and driven wheels; this is the work done by the hydraulic press during speed change. The power exerted is converted into the power for the driven wheel to rotate clockwise. In this gearbox, this includes the rotation of the driving and driven wheels around their own bearings, and the rotation of the ratchet sprockets branching off the driving and driven wheels around their own bearings.The partial residual ratchet chain displacement was completed, and the friction generated during the displacement process was greatly reduced due to the effect of the bearing.

[0076] Thirdly, the tension adjustment device for the transmission belt 4 is problematic because the drive pulley 14 and driven pulley 15 are not circular, but rather polygonal rhomboid. For example, if the drive pulley 14 rotates 60 degrees in one cycle, the length of the transmission belt 4 it needs to wind around varies depending on the angle reached during each cycle. The driven pulley 15 follows the same rule, and because the operating frequencies of the drive pulley 14 and driven pulley 15 are different, the transmission belt will continuously experience periods of slack and tension. Furthermore, due to the structural design of this transmission, the drive pulley 14 and driven pulley 15 have different radius ratios, resulting in varying requirements for the length of the transmission belt 4 at different times. Because of these factors, if the length of the transmission belt 4 were fixed, it would become either too taut or too slack. An overly taut transmission belt 4 would hinder the operation of the transmission. The transmission belt 4 is too slack, which is detrimental to the engagement of the pawl 16 and the ratchet chain 12. This creates a tricky problem in the customization of the transmission belt 4's length. To solve this problem, in this transmission, the radius of the drive pulley 14 and the radius of the driven pulley 15 can be appropriately adjusted with a small amount of floating extension and contraction based on a certain distance, in order to balance the tension of the transmission belt 4. On the drive pulley 14 and the driven pulley 15, springs are installed on the sliding blocks 9 connected to the two ends of each branch ratchet sprocket. Utilizing the extension and contraction properties of the springs, the radius of each branch ratchet sprocket from its respective axle 3 can be varied as needed within a certain short allowable range. This satisfies the transmission belt 4's length requirements under various conditions and keeps the transmission belt 4 in a moderately taut state. Each sliding block 9, installed in the slotted holes 13 on the driving wheel 14 and driven wheel 15, is divided into two sections. One section is connected to the shaft of its respective branch sprocket, while the other section has a concave groove that connects to its corresponding pyramid. Each spring is positioned between the two sections of the sliding block in its respective slotted hole 13. During the operation of the gearbox, its transmission belt 4 can be divided into two sections.

[0077] 1. The section of the transmission belt 4 where the power source 1 applies force: During the load-bearing process of the transmission, the section of the transmission belt 4 between the counterclockwise direction of the pawl 16 meshing with the drive pulley 14 and the clockwise direction of the pawl 16 meshing with the driven pulley 15 is precisely the section of the transmission belt 4 where the power source 1 applies force. A tension is generated in this section of the transmission belt 4, forcing springs installed in the slots 13 on the branch ratchet sprockets 5 attached to this section to compress accordingly based on the degree of tension of this section of the transmission belt 4. In other words, the radius of these branch ratchet sprockets 5 from their respective axle 3 is shortened due to the tension generated by the power source 1.

[0078] 2. The section of the transmission belt 4 where the power source does not apply force: This is the section of the transmission belt 4 outside the section where the power source does not apply force. The distance between each branch ratchet sprocket 5 and its corresponding radius r from the main shaft 3 is almost unaffected by the force applied by the power source. In essence, during the load-bearing process of the transmission, the distance between each branch ratchet sprocket 5 outside the section where the power source 1 applies force and its corresponding radius r from the main shaft 3 is determined by the tension of this section of the transmission belt. This process is accomplished by the springs installed on the slots 1 of each branch ratchet sprocket 5 on this section of the transmission belt 4, allowing for appropriate extension and retraction.

[0079] This continuously variable transmission (CVT) has a wide range of applications, from small bicycles to large vehicles, as well as winches, cranes, and more.

[0080] When the vehicle needs to move forward, the power from power source 1 can be switched to the drive wheel 14, while the load is switched to the driven wheel 15, and the power source can be switched to clockwise rotation to complete the forward movement of the vehicle.

[0081] For example, when the vehicle needs to reverse, the power of the power source 1 can be switched to the driven wheel 15, while the load is switched to the driving wheel 14, and the power source can be switched to counterclockwise rotation, which can also complete the reversing of the vehicle.

[0082] Sometimes, acceleration control is needed when vehicles are going downhill, when cranes are lowering loads, or when winches are lowering loads. This continuously variable transmission (CVT) can control acceleration in these situations.

[0083] For example, when the vehicle is going downhill, ① the power from power source 1 can be switched to the driven wheel 15, while power source 1 continues to rotate clockwise, but the load is switched to the driving wheel 14. The acceleration of the vehicle falling becomes the driving force, and power source 1 becomes the load resistance. ② The radius of the driven wheel 15 can be reduced as needed, while the radius of the driving wheel 14 can be increased, thus achieving the effect of acceleration control.

[0084] For example, when a crane is lowering a load, when a winch's load is falling from above, and when a vehicle is reversing on a wave surface, it is necessary to: ① Change the power source 1 on the drive wheel 14 to rotate counterclockwise. In this case, the load on the driven wheel 15 pulls the transmission belt to rotate counterclockwise, and the power source 1 on the drive wheel 14 becomes the load resistance of the transmission. ② Reduce the radius of the drive wheel 14 as needed, and at the same time increase the radius of the driven wheel 15, thereby achieving the effect of acceleration control and vehicle reversal.

[0085] The various embodiments of the present invention have been described above.

[0086] The above description is exemplary and not exhaustive, and is not limited to the disclosed embodiments. Many modifications and variations will be apparent to those skilled in the art without departing from the scope and spirit of the described embodiments. The terminology used herein is chosen to best explain the principles, practical application, or technical improvements to the embodiments in the market, or to enable others skilled in the art to understand the embodiments disclosed herein.

Claims

1. A ratchet chain continuously variable transmission (CVT), characterized in that, The system includes a power source (1); a hydraulic pump (2); a drive wheel (14); a driven wheel (15); and a transmission belt (4). The drive wheel (14) and the driven wheel (15) have basically the same structure, consisting of a main shaft and wheel assembly, a branch ratchet sprocket assembly, and a pyramid. The power source (1) is axially connected to the drive wheel (14) to provide power to the drive wheel (14). Both the drive wheel (14) and the driven wheel (15) have several pawls (16) arranged in the middle position along the circumference. The transmission belt (4) has ratchet teeth in the middle position on the inner wall of the inner wall. At least one ratchet tooth of the drive wheel (14) and the driven wheel (15) has a ratchet tooth in the middle position. The claw (16) engages with the ratchet; both the driving wheel (14) and the driven wheel (15) have several V-belt grooves (18) arranged on both sides of the circumference; V-belts (19) are provided on both sides of the transmission belt (4) to reduce the friction between the ratchet chain and the support surface when the ratchet chain makes local displacement along the circumference of the driving wheel and the driven wheel during the speed change process; a radius adjustment device pyramid is also provided on the axle (3) of each of the driving wheel (14) and the driven wheel (15); the output end of the hydraulic pump (2) is connected to the radius adjustment device pyramid through a bearing (7) to control the radius adjustment device pyramid.

2. A toothed belt continuously variable transmission as claimed in claim 1, characterized in that, The main shaft and wheel assembly includes a wheel axle (3) and two wheel discs (11); the two wheel discs (11) are exactly the same size and shape; there is a shaft hole at the center of the wheel disc (11) that matches the cross-section of the wheel axle; there are strip holes (13) on the wheel disc, the included angle between each adjacent strip hole (13) is 60 degrees, and the length distance of each strip hole (13) from the center of the wheel disc is equal to the radius length distance of the wheel attached to the wheel axle (3). The two wheel discs (11) are inserted into the shaft from both ends of the shaft respectively; the wheel attached to the shaft is sandwiched in the middle, the two wheel discs (11) are parallel to each other and perpendicular to the wheel axle (3), and are also used to limit the running trajectory of the conveyor belt.

3. A toothed belt continuously variable transmission as claimed in claim 2, characterised in that, Both the driving wheel (14) and the driven wheel (15) are provided with several branch ratchet sprocket assemblies along the circumference; each branch ratchet sprocket assembly includes a pair of sliding blocks (9) and a branch ratchet sprocket (5). The branch ratchet sprocket (5) is composed of a small shaft, a pawl (16), a triangular belt groove (18), and sliding blocks (9). The pawl (16) is arranged in the middle position of the small shaft. The two triangular belt grooves (18) containing bearings are respectively fitted on the two ends of the small shaft. The two sliding blocks (9) are respectively placed on the two ends of the small shaft. The lines connecting the two sliding blocks (9) connected to the same branch ratchet sprocket (5) and the two ends of the small shaft of the branch ratchet sprocket (5) are perpendicular and parallel to the wheel surface of the branch ratchet sprocket (5). The distance between the two sliding blocks (9) is equal to the distance between the two wheel discs (11) on the wheel disc assembly. The distance between the two sides of the sliding block (9) is provided with convex arc edges, which match the concave arc grooves on the two sides of the strip hole (13). The shafts at both ends of each branch ratchet sprocket (5) are inserted into a pair of corresponding strip holes (13) through a pair of sliding blocks (9). The branch ratchet sprocket (5) is located between the two discs (11). The shafts at both ends of each branch ratchet sprocket (5) are respectively located in a pair of corresponding strip holes (13). The small shaft and the main shaft of the branch ratchet sprocket (5) are parallel to the wheel axle (3) on the disc assembly, which is used for the sliding block (9) to carry the branch ratchet sprocket (5) to run back and forth along the track of the strip hole (13). The two sliding blocks (9) connected to the same branch ratchet sprocket (5) are inserted into a pair of corresponding strip holes (13) for each branch sprocket to slide back and forth along the track and adjust the radius distance.

4. A toothed belt continuously variable transmission as claimed in claim 3, characterised in that, Each of the sliding blocks (9) consists of two supporting sliders and a return spring connected together. The return spring is used to adjust the tension of the conveyor belt.

5. A toothed belt continuously variable transmission as claimed in claim 4, characterised in that, The same sliding block (9) has two branch sliding blocks (9), one of which is connected to the shaft end of the small shaft, and the other branch sliding block (9) has a trapezoidal hole. The two sliding blocks (9) on the same branch ratchet sprocket (5) have different lengths. The line connecting the grooves of each pair of sliding blocks (9) and the line connecting the two ends of the main shaft form an angle.

6. A toothed belt continuously variable transmission as claimed in claim 5, characterised in that, The conveyor belt (4) includes three ratchet chains (12) and two triangular belts (19); the two triangular belts (19) are arranged on both sides of the cross-section of the conveyor belt, and the three ratchet chains (12) are connected to the two triangular belts (19) by pins (17). The three ratchet chains (12) have the same number of ratchet segments. The ratchet arrangement direction of the two ratchet chains (12) on the secondary side of the conveyor belt is opposite to the ratchet arrangement direction of the ratchet chain (12) in the middle layer of the conveyor belt. The two ratchet chains (12) on the secondary side of the conveyor belt and the drive wheel (14) are equipped with pawls (16) to cooperate. The ratchet chain (12) in the middle layer of the conveyor belt and the driven wheel (15) are equipped with pawls (16) to cooperate.

7. The toothed belt continuously variable transmission device as set forth in claim 1, characterized by The radius adjustment device pyramid consists of a flange, six right-angled triangular steel blocks (6), and a section of steel pipe (10). The radius of the flange center hole and the radius of the steel pipe are equal, both fitted onto the axle (3), and can slide back and forth relative to the line connecting the two ends of the axle (3). Each section of the hypotenuse of the right-angled triangular steel block (6) has the same trapezoidal shape protruding, and the hypotenuse face is the lower base of the trapezoid. The right-angled triangular steel blocks (6) are distributed and fixed on one side of the flange. The short right-angled side of the right-angled triangular steel block (6) is connected to the flange face. Its right angle is close to the center of the flange. The intersection point of its hypotenuse and the short right-angled side is close to the circumference of the flange, and the face of each right-angled triangular steel block (6) is perpendicular to the flange face. The steel pipe (10) is vertically fixed on the center hole of the other side of the flange and is used to drive the handle of the radius adjustment device pyramid.

8. A toothed belt continuously variable transmission as claimed in claim 7, characterised in that The right-angled triangular steel blocks (6) inserted into the strip holes (13) on the pyramid have hypotenuse angles that coincide with the angles formed by the lines connecting the grooves of the pairs of sliding blocks (9) and the axial direction, which are complementary angles. At the same time, the recessed trapezoidal grooves of each sliding block (9) also coincide with the protruding trapezoidal cross-sections on the hypotenuse of the pyramid. Therefore, the protruding trapezoidal cross-sections of the hypotenuses of the right-angled triangular steel blocks (6) on the pyramid can be inserted into the trapezoidal recesses of their respective pairs of sliding blocks (9), which serves to: when the actuation source drives the pyramid handle, so that the right-angled triangular steel blocks (6) on the pyramid enter the strip holes (13) from shallow to deep, it is also the right-angled triangular steel blocks (6) of the pyramid. As the trapezoidal cross-section on the hypotenuse of the triangular steel block (6) increases in radius space to the center of the wheel axle (3), the lower base of the trapezoidal cross-section on the hypotenuse of each right-angled triangular steel block (6) on the pyramid pushes the radius of each branch ratchet sprocket (5) to increase. When the actuator drives the pyramid handle, the right-angled triangular steel block (6) on the pyramid retracts from the deep to the shallow of each strip hole (13), and the trapezoidal cross-section on the side of each right-angled triangular steel block (6) on the pyramid decreases in radius space to the center of the axis. As a result, the two waist sides of the trapezoidal cross-section on the hypotenuse of each right-angled triangular steel block (6) on the pyramid pull the radius of each branch ratchet sprocket (5) to shorten.

9. A toothed belt continuously variable transmission as claimed in claim 8, characterised in that, The driving wheel and the driven wheel are each equipped with a pyramid. The handles of the two pyramids are made of steel pipes (10) with opposite orientations. Each pyramid is connected to the output shaft of the hydraulic pump (2) via a bearing (7) and a rod (8). The rod (8) is fixed with a hydraulic pump (2) on its upper and lower sides. The pumps (2) are used as radius adjustment devices on the driving wheel and the driven wheel. They are bundled together and share the same braking device to adjust the radius of the driving wheel and the driven wheel inversely.

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