Continuous variable torque transmission mechanism with infinite gear ratio

Abstract

Continuous Variable Torque Transmission Mechanism with Infinite Gear Ratio A continuously variable torque transmission mechanism with infinite gear ratio disclosed in the present invention comprises a linear guide (1), a square shaft (2), a linear slide bearing (3), a crank shaft (4), a connecting rod (5), a double hinge bush (6), a slider shaft (7), an oscillation arm (8), an oscillation shaft (9), three bevel gears (10, 11, and 12), a one-way bearing 1 (10a), a one-way bearing 2 (11a) and two gears (one for output power and one for input power) (13 and 14) to facilitate continuous and precise control over both torque and gear ratio, enabling highly adaptable and efficient power transfer in a wide range of applications

Description

[0001] TITLE OF THE INVENTION

[0002] Continuous Variable Torque Transmission Mechanism with Infinite Gear Ratio

[0003] FIELD OF THE INVENTION

[0004] The present invention relates to the field of mechanical power transmission systems and, more specifically, to a novel continuous variable torque transmission mechanism with infinite gear ratio. This invention is directed toward transmission mechanisms designed to facilitate continuous and precise control over both torque and gear ratio, enabling highly adaptable and efficient power transfer in a wide range of applications.

[0005] BACKGROUND OF THE INVENTION

[0006] The field of mechanical power transmission has relied on conventional transmission systems characterized by fixed gear ratios with distinct steps, such as gears and gearboxes. These systems provide a predefined set of gear ratios, each associated with a specific combination of speed and torque. However, the inherent limitations of these traditional transmission systems become evident when operational requirements fall between these predetermined gear ratios. This constraint can impede adaptability and efficiency in a wide array of applications, ranging from automotive vehicles to industrial machinery and robotics. Such limitations are most palpable in the domains of automotive vehicles, industrial machinery, and robotics, where optimal performance and flexibility are paramount. The constraints imposed by fixed gear ratios can lead to inefficiencies, performance bottlenecks, and suboptimal results in a host of scenarios.

[0007] In an attempt to mitigate these limitations, continuously variable transmissions (CVTs) have been introduced. CVTs offer a range of gear ratios, but their adaptability is confined to a finite, predefined spectrum. While an improvement over traditional systems, they still fall short of providing the level of continuous, infinite variability in both gear ratio and torque transmission as envisioned by the invention presented in this patent application.

[0008] One such innovation, as disclosed in JP2006183780A, presents a unit input shaft connected to a motor and linked to a toroidal continuously variable transmission mechanism and a constant transmission mechanism, allowing for continuous changes in transmission gear ratio. This patent describes an infinitely variable gear ratio transmission, emphasizing the importance of maintaining the total transmission ratio of the continuously variable transmission at a geared neutral point.

[0009] JP2006183780A introduces an advanced system comprising shift position detection, accelerator depression measurement, and vehicle speed monitoring mechanisms. These components work in conjunction with an actuator responsible for adjusting the gear ratio based on the detected parameters. By calculating the target motor output torque value, the system ensures precise control of the motor's output torque.

[0010] However, it is important to note that JP2006183780A, like many existing solutions, may have certain limitations. One limitation is that the system's complexity and reliance on various sensors and actuators can introduce points of potential failure, maintenance, and increased manufacturing costs. Additionally, maintaining gear ratios at specific points, as demonstrated in JP2006183780A, may be constrained within finite ranges and might not fully satisfy the need for continuous and infinitely variable gear ratios.

[0011] These prior art systems, including JP2006183780A, highlight the ongoing efforts in the industry to enhance the adaptability and efficiency of mechanical power transmission systems, especially in the context of automotive and industrial applications.

[0012] In light of the inherent constraints of traditional fixed gear ratios and the finite-range adaptability of CVTs, the need for a more comprehensive solution becomes increasingly evident. The evolving landscape of technology and industry demands a transmission system that transcends these historical limitations.

[0013] To address the need for a more comprehensive solution, the current invention introduces a Continuous Variable Torque Transmission with Infinite Gear Ratio. This novel transmission system stands out by enabling the seamless and infinite adjustment of the gear ratio while allowing for precise control of torque across a wide operational spectrum. Such an innovation promises to revolutionize the field of mechanical power transmission, ensuring optimal performance, efficiency, and adaptability in a diverse range of applications, from high-performance automotive systems to precision machinery and beyond.

[0014] OBJECT OF THE INVENTION

[0015] The principal object of the present invention is to provide a continuous variable torque transmission mechanism with infinite gear ratio, enabling versatile and precise power transmission adaptable to a broad spectrum of applications.

[0016] Another object of the present invention is to offer a transmission mechanism that transcends the limitations of traditional systems and finite-range CVTs, allowing for seamless and infinite adjustments to the gear ratio and control over torque.

[0017] Yet another object of the present invention is to enhance the efficiency, performance, and versatility of mechanical power transmission systems, contributing to advancements in energy efficiency, reduced mechanical stress, and superior performance across various industrial and automotive domains.

[0018] Another object of the present invention is to enable power transmission systems to seamlessly adapt to variable operational conditions. Yet another object of the present invention is providing the means for mechanical systems to adjust their performance characteristics in real-time, ensuring optimal operation in a dynamic and changing environment.

[0019] Yet another object of the present invention is offering precise control over power transmission, suitable for a wide range of applications.

[0020] A further object of the present invention is to minimize mechanical wear and tear in power transmission components by enabling precise control over both gear ratio and torque, it seeks to reduce the strain on mechanical parts, prolonging their lifespan and enhancing the overall reliability of the system.

[0021] SUMMARY OF THE INVENTION

[0022] The invention disclosed in this application pertains to a continuously variable torque transmission mechanism with an infinite gear ratio. This innovative mechanism comprises several key components to facilitate its operation, including a linear guide, square shaft, linear slide bearing, crank shaft, connecting rod, double hinge bush, slider shaft, oscillation arm, oscillation shaft, bevel gears, and input and output power gears.

[0023] The operation of the mechanism is initiated by the input power gear, which transmits rotational motion to the square shaft through the crank shaft and connecting rod. The square shaft is supported by the linear slide bearing, which ensures its smooth and precise linear motion along the linear guide. The slider shaft is connected to the square shaft and oscillates back and forth, driven by the crank mechanism.

[0024] The oscillation of the slider shaft is a key aspect of this invention, and it is enabled by the double hinge bush, allowing the slider shaft to oscillate while maintaining a constant distance from the linear guide. This oscillation drives the oscillation arm and, in turn, two bevel gears, which rotate in opposite directions. The relative speeds of these bevel gears determine the overall gear ratio of the mechanism, offering continuous variability. By adjusting the position of the slider shaft on the oscillation arm, the gear ratio of the mechanism can be changed infinitely. This innovative transmission system provides exceptional adaptability and precision in controlling both torque and gear ratio, making it a valuable addition to a wide range of applications in the fields of automotive, industrial machinery, robotics, and more. This invention represents a significant advancement in mechanical power transmission, offering limitless gear ratio possibilities, and it has the potential to enhance efficiency and performance across various domains.

[0025] BRIEF DESCRIPTION OF THE DRAWINGS

[0026] The features of the invention as per the present patent application are described with reference to the following drawings in which like elements are labeled similarly. The present invention will be more clearly understood from the detailed description and the accompanying drawings, wherein:

[0027] FIG. 1 shows an isometric view of a continuous variable torque transmission mechanism with infinite gear ratio.

[0028] FIG. 2 shows an isometric view of a continuous variable torque transmission mechanism with infinite gear ratio.

[0029] FIG. 3 shows an exploded isometric view of a continuous variable torque transmission mechanism with infinite gear ratio.

[0030] FIG. 4 shows an isometric view of an oscillation arm assembly of the present invention.

[0031] FIG. 5 shows an exploded isometric view of an oscillation arm assembly of the present invention.

[0032] FIG. 6 shows an isometric view of a crank shaft assembly of the present invention.

[0033] FIG. 7 shows an isometric view of a crank shaft assembly of the present invention.

[0034] FIG. 8 shows an exploded isometric view of the crank shaft assembly of the present invention. FIG. 9 shows an isometric view of a linear guide assembly of the present invention.

[0035] FIG. 10 shows an isometric view of a linear guide assembly of the present invention.

[0036] FIG. 11 shows a schematic diagram of the present invention.

[0037] FIG. 12 shows a schematic diagram of the present invention.

[0038] List of designations / reference numbers in figure

[0039] 1. Linear Guide

[0040] 2. Square Shaft

[0041] 3. Linear Slide Bearing

[0042] 4. Crank Shaft

[0043] 5. Connecting Rod

[0044] 6. Double Hing Bush

[0045] 7. Slider Shaft

[0046] 8. Oscillation Arm

[0047] 9. Oscillation Shaft

[0048] 10. Bevel Gear 1 (Clock wise Rotation)

[0049] 10a. One-way bearing 1

[0050] 11 . Bevel Gear 2 (Anti-Clockwise Rotation)

[0051] 11 a. One-way bearing 2

[0052] 12. Bevel Gear 3

[0053] 13. Gear (Output Power)

[0054] 14. Gear (Input Power)

[0055] 15. Base

[0056] DETAILED DESCRIPTION OF THE INVENTION

[0057] The following description of the preferred embodiment(s) is merely exemplary in nature and is in no way intended to limit the invention, its application, or its uses.

[0058] The description of illustrative embodiments according to principles of the present invention is intended to be read in connection with the accompanying drawings, which are to be considered as a part of the entire written description.

[0059] In the description of embodiments of the invention disclosed herein, any reference to direction or orientation is merely intended for convenience of description and is not intended in any way to limit the scope of the present invention. Relative terms and directives thereof are for convenience of description only and do not require that the apparatus be constructed or operated in a particular manner unless explicitly indicated as such. Terms such as “attached,” “affixed,” “connected,”, “coupled,” “interconnected,” and similar references to a relationship wherein structures are secured or attached either directly or indirectly through intervening structures, as well as both movable or rigid attachments or relationships, unless expressly described otherwise. Moreover, the features and benefits of the invention are illustrated by reference to the exemplified embodiments.

[0060] Accordingly, the invention expressly should not be limited to such exemplary embodiments illustrating some possible non-limiting combination of features that may exist alone or in other combinations of features; the scope of the invention being defined by the claims appended hereto.

[0061] The present invention discloses a continuous variable torque transmission mechanism with infinite gear ratio to facilitate continuous and precise control over both torque and gear ratio, enabling highly adaptable and efficient power transfer in a wide range of applications.

[0062] In order to describe each essential component efficiently and particularly, the present invention has been divided in the three major assemblies based on their function and position:

[0063] • Crank shaft assembly

[0064] • Oscillation arm assembly

[0065] • Linear guide assembly

[0066] Crank shaft assembly mainly comprises a square shaft (2), a linear slide bearing (3), a crank shaft (4), a connecting rod (5), a double hinge bush (6), a slider shaft (7).

[0067] Oscillation arm assembly mainly comprises an oscillation arm (8), an oscillation shaft (9), a one-way bearing 1 (10a), a one-way bearing 2 (1 1 a), three bevel gears (10, 1 1 , and 12).

[0068] Linear guide assembly mainly comprises a linear guide (1 ), a base (15).

[0069] The FIG.1 shows an isometric view of a continuously variable torque transmission mechanism with infinite gear ratio. The mechanism comprising of the linear guide (1 ), the square shaft (2), the linear slide bearing (3), the crank shaft (4), the connecting rod (5), the double hinge bush (6), the slider shaft (7), the oscillation arm (8), the oscillation shaft (9), three bevel gears (10, 1 1 , and 12), and two gears (one for output power and one for input power) (13 and 14).

[0070] The linear guide (1 ) provides a smooth and accurate linear motion for the crank shaft assembly. The square shaft (2) is used to transmit power from the gear (input power) (14) to the crank shaft (4). The linear slide bearing (3) supports the crank shaft assembly and allows it to move freely along the linear guide (1 ). The crank shaft (4) converts the rotational motion of the square shaft (2) into linear motion of the slider shaft (7). The connecting rod

[0071] (5) connects the crank shaft (4) to the slider shaft (7). The double hinge bush

[0072] (6) allows the slider shaft (7) to oscillate while maintaining a constant distance from the linear guide (1 ). The slider shaft (7) oscillates back and forth, driving the oscillation arm (8).

[0073] The oscillation arm (8) is connected to the oscillation shaft (9) which drives bevel gear 1 (10) and bevel gear 2 (1 1 ). The bevel gear 1 (10) is mounted with the one-way bearing 1 (10a) (ref. FIG.5) and the bevel gear 2 (1 1 ) is mounted with the one-way bearing 2 (1 1 a) (ref. FIG.5), on the oscillation shaft (9). The bevel gear 1 (10) and the bevel gear 2 (1 1 ) are engaged with the bevel gear 3 (12) at a right angle (i.e., at 90° angle). The bevel gear 3 (12) drives the gear (output) (13). The power is transmitted through the bevel gear 1 (10) to the bevel gear 3 (12) when the bevel gear 1 (10) rotates in a clockwise direction and the power is transmitted through the bevel gear 2 (1 1 ) to the bevel gear 3 (12) when the bevel gear 2 (1 1 ) rotates in an anticlockwise direction.

[0074] When the slider shaft (7) moves in the outward direction, the oscillation arm

[0075] (8) oscillates in a clockwise direction. This movement drives oscillation shaft

[0076] (9) to rotate in a clockwise direction. Hence, this drives bevel gear 1 (10) and bevel gear 2 (1 1 ) to rotate in a clockwise direction and bevel gear 3 (12) to rotate in an anti-clockwise direction. However, the one-way bearing 2 (1 1 a) allows bevel gear 2 (1 1 ) to rotate freely in an anti-clockwise direction, by disengaging it from the oscillation shaft (9) to avoid locking with the bevel gear 3 (12).

[0077] If the slider shaft (7) were to move in the inward direction, the oscillation arm (8) would oscillate in an anti-clockwise direction. Which leads to the rotation of the oscillation shaft (9) in an anti-clockwise direction. This would drive bevel gear 1 (10) and bevel gear 2 (11 ) to rotate in an anti-clockwise direction and bevel gear 3 (12) to rotate in an anti-clockwise direction. However, the one-way bearing 1 (10a) allows bevel gear 1 (10) to rotate freely in a clockwise direction, by disengaging it from the oscillation shaft (9) to avoid locking with the bevel gear 3 (12). By varying the position of the slider shaft (7) on the oscillation arm (8), the gear ratio can be changed infinitely.

[0078] FIG.2 depicts an isometric view of a continuous variable torque transmission mechanism with infinite gear ratio, where the crank shaft assembly is at the lowest position on the oscillation arm (8). In such case, the revolutions per minute on the gear (output power) (13) is maximum and torque is minimum. In opposite case wherein the crank shaft assembly is at the highest position (ref. FIG.1 ) on the oscillation arm (8), the revolutions per minute on the gear (output power) (13) is minimum and torque is maximum. Central to its versatility is the ability for users to modify the position of the crank shaft assembly on the oscillation arm (8), enabling precise adjustments to torque and RPM characteristics. To initiate this user- controlled adjustment, an accessible mechanism is thoughtfully integrated, allowing for the shifting of the crank shaft assembly's position along the oscillation arm (8). This positioning control can be achieved manually or, in certain applications, can be automated for dynamic and real-time adaptations. Whether through manual manipulation or automated systems, users have the flexibility to fine-tune the position of the crank shaft assembly at any given point during operation.

[0079] This dynamic positioning feature allows users to continuously adapt and fine-tune the mechanism's gear ratios, accommodating an extensive range of operational scenarios. Whether requiring high-speed, low-torque performance or low-speed, high-torque power transfer, the user-initiated positioning control empowers precise adjustments to meet the specific demands of diverse applications. Thus, the mechanism serves as an innovative and user-centric solution for industries where varying torque and RPM are essential for optimal performance and efficiency.

[0080] FIG.3 presents an exploded isometric view of the continuous variable torque transmission mechanism, providing an intricate portrayal of all its essential components and their spatial relationships. This exploded view aims to elucidate the internal structure and functioning of the system, highlighting each component's role within the mechanism.

[0081] At the core of this mechanism lies the square shaft (2), a vital conduit for power transmission. The linear slide bearing (3) offers pivotal support to the square shaft (2), ensuring its smooth and precise linear motion along the linear guide (1 ). This linear guide (1 ) serves as the fundamental rail, guiding the motion of the square shaft (2) with remarkable accuracy.

[0082] The crank shaft (4) is the heart of motion conversion, translating the rotational movement initiated by the square shaft (2) into linear motion for the slider shaft (7). The connecting rod (5) acts as the intermediary link between the crank shaft (4) and the slider shaft (7), facilitating the transfer of motion and enabling the oscillatory movement essential for gear ratio adjustments.

[0083] The double hinge bush (6) is a critical element that permits the oscillation of the slider shaft (7) while maintaining a fixed distance from the linear guide (1 ). This oscillatory motion is central to the system's capability for infinite gear ratio adjustments, offering adaptability in torque and gear ratio control.

[0084] The oscillation arm (8) is a pivotal component that directly influences the rotation of bevel gear 1 (10) and bevel gear 2 (1 1 ). These gears are mounted on the oscillation shaft (9) along with one-way bearing 1 (10a) and one-way bearing 2 (1 1 a). This configuration allows for the dynamic interplay of these gears, influencing the overall gear ratio of the mechanism.

[0085] Bevel gear 3 (12) serves as the connector, engaging bevel gear 1 (10) and bevel gear 2 (1 1 ) at a right angle, driving the gear (output power) (13). The overall gear ratio, is achievable by adjusting the position of the slider shaft (7) on the oscillation arm (8).

[0086] This comprehensive exploded view underscores the intricate nature of the continuous variable torque transmission mechanism, offering a versatile, adaptable, and efficient means of power transmission. By revealing the interrelationships between these components, it showcases the innovative features that empower this mechanism to provide continuous and precise control over both torque and gear ratios, making it a valuable addition to a wide range of applications across industrial, automotive, and other domains.

[0087] FIG.4 offers an illuminating isometric view of the oscillation arm assembly, a pivotal component within the continuous variable torque transmission mechanism with an infinite gear ratio. At the heart of this assembly is the oscillation arm (8), a fundamental element that converts linear motion into rotational motion, playing a central role in the dynamic gear ratio control system. The oscillation arm (8) is seamlessly connected to the oscillation shaft (9), which serves as the pivotal axis for the arm's oscillatory movement. This back-and-forth oscillation is the key driver of the interconnected bevel gears' rotation.

[0088] FIG.5 illustrate two critical components, one-way bearing 1 (10a) and oneway bearing 2 (1 1 a), are meticulously mounted on the bevel gear 1 (10) and the bevel gear 2 (1 1 ). These one-way bearings play a crucial role by permitting unidirectional motion while preventing any undesired reverse rotation. One-way bearing 1 (10a) ensures that bevel gear 1 (10) rotates in the intended direction, while one-way bearing 2 (11 a) allows bevel gear 2 (1 1 ) to follow a specific unidirectional motion, essential for precise control. The assembly prominently features three bevel gears: bevel gear 1 (10), bevel gear 2 (1 1 ), and bevel gear 3 (12). Bevel gears 1 and 2 are intrinsically connected to the one-way bearings. Bevel gear 3 (12) serves as a critical transmission point, enabling power delivery to the output component of the mechanism.

[0089] The visual representation in FIG. 4 and FIG. 5 effectively highlights the intricate relationships and precise arrangement of these essential components within the oscillation arm assembly. This assembly serves as the central control hub for gear ratio adjustments within the mechanism. The oscillation arm's motion, driven by the oscillation of the slider shaft, triggers the interconnected components to work in tandem, ensuring that motion remains precise and unidirectional. This, in turn, allows for continuous adaptability in gear ratios and torque transmission, exemplifying the innovation and mechanical sophistication at the core of this inventive system.

[0090] FIG.6 presents the first part of the crank shaft assembly, a pivotal component within the continuous variable torque transmission mechanism designed for infinite gear ratio capabilities. This assembly plays a critical role in converting the rotational motion originating from the input shaft into precise linear motion, enabling meticulous control over torque and gear ratio adjustments. Specifically, this part of the assembly highlights key components, including the connecting rod (5), double hinge bush (6), and slider shaft (7).

[0091] The connecting rod (5) is a fundamental link in the assembly, responsible for connecting the crank shaft (4) to the slider shaft (7). Its role is essential in the mechanism's capacity to convert the rotational motion generated by the crank shaft (4) into the oscillatory motion of the slider shaft (7), a pivotal aspect of gear ratio adjustments. The double hinge bush (6) is another integral element in this assembly, allowing the oscillation of the slider shaft (7) while ensuring it maintains a constant distance from the linear guide (1 ). This unique feature is fundamental to achieving the infinite gear ratio capabilities of the mechanism, contributing to its adaptability and precision in power transmission. The slider shaft (7) stands at the core of this assembly, and its oscillatory movement is a defining characteristic. Enabled by the connecting rod (5) and double hinge bush (6), the slider shaft (7) plays a central role in driving the entire mechanism, facilitating gear ratio control and torque adjustments.

[0092] FIG.7 complements the preceding view by showcasing the second part of the crank shaft assembly, emphasizing the linear slide bearing (3) and the crank shaft (4). The linear slide bearing (3) holds a fundamental position within the assembly, providing crucial support for the square shaft (2) and ensuring its seamless and precise linear motion along the linear guide (1 ). This component is essential for the overall efficiency of the assembly, allowing for efficient power transfer and linear motion, both of which are critical for the mechanism's operation. The crank shaft (4) stands as a central component, bearing the responsibility of transforming the rotational motion generated by the input shaft into linear motion. This process forms the foundational basis for torque control and gear ratio adjustments within the system, making the crank shaft (4) an indispensable cornerstone of the inventive mechanism.

[0093] FIG.8 offers a detailed exploded view of the crank shaft assembly, a pivotal element within the continuous variable torque transmission mechanism equipped with infinite gear ratio capabilities. This view dissects the assembly to highlight the individual components, showcasing the intricate interplay of its parts. The central elements featured in this exploded view include the square shaft (2), the linear slide bearing (3), the crank shaft (4), the connecting rod (5), the double hinge bush (6), and the slider shaft (7).

[0094] The square shaft (2) serves as a key conduit for power transmission, connecting the input shaft to the entire assembly. It is the initial point where rotational motion from the input source is introduced into the mechanism. The linear slide bearing (3) is a fundamental component that supports the square shaft (2) as it moves along the linear guide (1 ). This support ensures the square shaft's smooth and precise linear motion, a vital characteristic for efficient power transfer.

[0095] The crank shaft (4) is a central element responsible for converting the rotational motion initiated by the square shaft (2) into linear motion. This conversion forms the basis for the control of torque and gear ratios within the system. The connecting rod (5) acts as the intermediary link between the crank shaft (4) and the slider shaft (7), facilitating the transfer of motion and enabling the oscillatory movement essential for gear ratio adjustments.

[0096] The double hinge bush (6) is another critical component that allows the slider shaft (7) to oscillate back and forth while maintaining a fixed distance from the linear guide (1 ). This oscillation is a pivotal aspect of the system's capability for infinite gear ratio adjustments. The slider shaft (7) stands as the central element in this assembly and plays a crucial role in driving the entire mechanism, translating the motion from the connecting rod (5) into oscillatory movement, thereby controlling torque and gear ratios precisely.

[0097] In this exploded view, the intricate relationship between these components is on full display, offering a detailed understanding of how each part contributes to the adaptability and efficiency of the entire system. The innovative nature of this crank shaft assembly is clearly showcased, demonstrating its ability to provide continuous and precise control over torque and gear ratios in a wide range of applications.

[0098] Together, FIG.6, FIG.7 and FIG.8 provide a comprehensive understanding of the components comprising the crank shaft assembly and their specific functions within the innovative system. They collectively exemplify the precision and mechanical sophistication embedded within this inventive system, enabling adaptability and efficiency in power transmission across a diverse array of applications.

[0099] FIG.9 and FIG.10 collectively present isometric views of the linear guide assembly, a critical element within the continuous variable torque transmission mechanism engineered for infinite gear ratio capabilities. This assembly is central to guiding and facilitating the linear motion required for efficient power transmission, enabling precise control over torque and gear ratio adjustments. In this description, we highlight the two core components within the linear guide assembly: the linear guide (1 ) and the base (15).

[0100] The linear guide (1 ) takes center stage as a foundational component within the assembly. It is tasked with providing a smooth and accurate linear motion for the entire mechanism. This pivotal role ensures that the square shaft (2) moves precisely along its length, free from friction and disturbances. The linear guide (1 ) serves as the guiding rail, facilitating the linear movement required for the transfer of power from the input shaft to the output. It guarantees an efficient and reliable linear motion, contributing to the adaptability and precision of the entire system.

[0101] Complementing the linear guide, the base (15) is a critical element that forms the sturdy foundation for the entire linear guide assembly. Its primary role is to anchor and support the linear guide (1 ), ensuring it remains securely in place. By providing stability and a fixed reference point, the base (15) plays a pivotal role in maintaining the structural integrity of the assembly. This stationary support is essential for enabling precise linear motion and, consequently, efficient power transmission. The base (15) embodies the reliability and stability required for the mechanism's adaptability and its capacity to offer continuous and precise control over torque and gear ratios.

[0102] FIG.11 offers a comprehensive schematic diagram of the present invention, showcasing its intricate components and their spatial relationships. The components featured in this diagram include the square shaft (2), the crank shaft (4), the connecting rod (5), the double hinge bush (6), the slider shaft (7), the oscillation arm (8), the oscillation shaft (9), bevel gears 1 (10) and 2 (1 1 ), and bevel gear 3 (12). This specific arrangement illustrates the slider shaft (7) at its lowest position on the oscillation arm (8), which has direct implications for the mechanical performance.

[0103] In this configuration, with the slider shaft (7) positioned at the lowest point on the oscillation arm (8), the mechanism operates to maximize the revolutions per minute (RPM) on the gear designated as the output power (13). This results in the output shaft spinning at its highest RPM, delivering maximum rotational speed to the system. However, it's essential to note that this setup simultaneously minimizes the torque output, making it the lowest within the range of possibilities provided by this inventive system.

[0104] This schematic diagram serves as a visual representation of one specific operating state of the invention, where the position of the slider shaft (7) directly influences the mechanical performance. By varying the position of the slider shaft (7) on the oscillation arm (8), users can precisely control the gear ratio, offering a wide range of RPM and torque possibilities. This adaptability is a central feature of the invention, enabling it to cater to a diverse array of applications where varying RPM and torque requirements are crucial for optimal performance. The figure underscores the innovative nature of this continuous variable torque transmission mechanism, offering adaptable and efficient power transmission across a broad spectrum of industrial and automotive domains.

[0105] FIG.12 offers a schematic diagram identical to that of FIG.1 1 , portraying the intricate components of the present invention and their spatial relationships. These components include the square shaft (2), the crank shaft (4), the connecting rod (5), the double hinge bush (6), the slider shaft (7), the oscillation arm (8), the oscillation shaft (9), bevel gears 1 (10) and 2 (11 ), and bevel gear 3 (12). However, in this representation, the slider shaft (7) is positioned at the highest point on the oscillation arm (8), which imparts distinct mechanical characteristics to the system.

[0106] In this configuration, with the slider shaft (7) elevated to the highest position on the oscillation arm (8), the mechanism operates to minimize the revolutions per minute (RPM) on the gear designated as the output power (13). Consequently, the output shaft experiences the lowest rotational speed, delivering maximum torque output. This setup prioritizes torque generation, making it the highest within the spectrum of possibilities offered by this inventive system.

[0107] This schematic diagram serves as a visual representation of a specific operational state of the invention, emphasizing how the position of the slider shaft (7) significantly influences the mechanical performance. By adjusting the position of the slider shaft (7) on the oscillation arm (8), users gain precise control over the gear ratio, enabling a broad range of RPM and torque possibilities. This adaptability is a central feature of the invention, empowering it to meet the diverse RPM and torque requirements of various applications, where optimal performance demands high torque and lower RPM. This figure underscores the ingenuity of this continuous variable torque transmission mechanism, offering adaptable and efficient power transmission across a wide array of industrial and automotive domains.

Claims

CLAIMSWe Claim:1 . A continuously variable torque transmission mechanism with infinite gear ratio, characterized in that wherein, the said mechanism comprising:• a linear guide (1 );• a square shaft (2) slidably mounted on the linear guide (1 ) and used to transmit power from a gear (input power) (14) source to a crank shaft (4);• a linear slide bearing (3) supporting the square shaft (2) and allowing it to move freely along the linear guide (1 );• the crank shaft (4) rotatably mounted on the linear slide bearing (3) and converting the rotational motion of the square shaft (2) into linear motion of a slider shaft (7);• a connecting rod (5) connecting the crank shaft (4) to the slider shaft (7);• a double hinge bush (6) allowing the slider shaft (7) to oscillate while maintaining a constant distance from the linear guide (1 );• an oscillation arm (8) connected to the slider shaft (7);• an oscillation shaft (9) connected to the oscillation arm (8);• a bevel gear 1 (10) mounted on the oscillation shaft (9) using a one-way bearing 1 (10a), said bevel gear 1 (10) being in mesh with a bevel gear 3 (12);• a bevel gear 2 (1 1 ) mounted on the oscillation shaft (9) using a one-way bearing 2 (1 1 a), said bevel gear 2 (1 1 ) being in mesh with the bevel gear 3 (12); and• a gear (output power) (13) connected to the bevel gear 3 (12);• wherein the oscillation of the slider shaft (7) drives the oscillation arm (8) and the oscillation shaft (9), causing the bevel gear 1 (10) and the bevel gear 2 (1 1 ) to rotate;• wherein the one-way bearing 1 (10a), mounted on the oscillation shaft (9), allows bevel gear 1 (10) to rotate freely ina clockwise direction when the slider shaft (7) moves inward, by disengaging it from the oscillation shaft (9) to avoiding locking with bevel gear 3 (12);• wherein the one-way bearing 2 (1 1 a), mounted on the oscillation shaft (9), allows bevel gear 2 (11 ) to rotate freely in an anti-clockwise direction when the slider shaft (7) moves outward, by disengaging it from the oscillation shaft (9) to avoid locking with bevel gear 3 (12);• wherein the position of the slider shaft (7) on the oscillation arm (8) can be adjusted to change the gear ratio infinitely, thereby providing continuous and precise control over both torque and gear ratio.

2. The continuously variable torque transmission mechanism with infinite gear ratio as claimed in claim 1 , wherein the linear guide (1 ) is provided with a coating to reduce friction and wear.

3. The continuously variable torque transmission mechanism with infinite gear ratio as claimed in claim 1 , wherein the square shaft (2) is provided with a keyway to ensure positive engagement with the gear (input power) (14).

4. The continuously variable torque transmission mechanism with infinite gear ratio as claimed in claim 1 , wherein the linear slide bearing (3) is pre-loaded to reduce play and ensure accurate positioning of the crank shaft assembly.

5. The continuously variable torque transmission mechanism with infinite gear ratio as claimed in claim 1 , wherein the connecting rod (5) is adjustable in length, allowing fine-tuning of the transmission mechanism for different applications.

6. The continuously variable torque transmission mechanism with infinite gear ratio as claimed in claim 1 , wherein the double hingebush (6) comprises a friction-reducing material to minimize wear and increase the operational lifespan of the mechanism.

7. The continuously variable torque transmission mechanism with infinite gear ratio as claimed in claim 1 , wherein the one-way bearing 1 (1 Oa) and the one-way bearing 2 (1 1 a) are adjustable to control the engagement and disengagement thresholds, thereby allowing customization of torque transfer characteristics.

8. The continuously variable torque transmission mechanism with infinite gear ratio as claimed in claim 1 , wherein the oscillation arm (8) is adjustable in length, providing variability in the mechanical advantage and contributing to the adaptability of the gear ratio.

9. The continuously variable torque transmission mechanism with infinite gear ratio as claimed in claim 1 , wherein the gear (input power) (14) is part of a modular system, allowing easy replacement and customization for different power sources.

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