Compact reciprocating kneading transmission mechanism

Abstract

The application discloses a compact reciprocating kneading transmission mechanism, comprising a mounting box, a main driving mechanism, a first output mechanism and a second output mechanism, wherein the main driving mechanism comprises a motor, a driving worm and a main driving shaft connected through a steering transmission part, the driving worm is arranged vertically to the main driving shaft, and the axis of the main driving shaft is innovatively arranged to extend along the maximum diagonal direction of the internal space of the mounting box, so that the maximum effective length is obtained in the limited volume, and the utmost compactness is realized; the main driving shaft simultaneously drives the first output mechanism and the second output mechanism, and the two output rotary motions with different speed reduction ratios through different transmission paths. Through the three-dimensional space layout optimization, the highly integrated integrated structure and the low-noise transmission pair selection, the volume minimization, the operation reliability improvement and the noise suppression are comprehensively realized.

Description

Technical Field

[0001] This invention relates to the field of mechanical transmission technology, specifically to a compact reciprocating kneading transmission mechanism. Background Technology

[0002] In many devices that require precise linear reciprocating motion (such as certain automated actuators, adjustable support devices, massage equipment, etc.), a compact transmission mechanism is typically needed to enable the core functional components to move smoothly and accurately along a pre-set guide rail. This type of transmission mechanism is essentially an integrated linear transmission system, and its performance directly determines the device's operating range, operational stability, noise level, and overall reliability.

[0003] One typical application scenario is its integration into the interior of passenger vehicle seats (such as car seats) where space is extremely limited and operational quality requirements are stringent, to drive the reciprocating motion of a functional module. In this scenario, due to the extremely compressed installation space, the continuous vibration of the operating environment, and the extremely high requirements for quietness, the design of this transmission mechanism presents comprehensive challenges far exceeding those of ordinary industrial or household environments, including the following points.

[0004] First, there is the extreme spatial constraint: the entire transmission chain, including the drive source, power reduction and conversion unit, and guiding and load-bearing structures, must be accommodated within an extremely thin installation cross-section. This requires fundamental innovative design of the transmission mechanism in terms of structural integration and compact component layout. Traditional linear transmission solutions are often bulky and difficult to apply directly.

[0005] Secondly, there is the dual requirement of high load and high reliability: to drive the functional modules to complete the predetermined actions, the transmission mechanism must continuously output sufficient thrust and torque within a limited volume, and be able to work stably for a long time under the harsh conditions of vehicle vibration. This places extreme demands on the reliability of the connection structure of the key transmission components of the system.

[0006] Thirdly, extreme suppression of mechanical noise: To ensure the quietness of the operating environment, any mechanical noise generated by the transmission mechanism during operation (such as gear meshing impact, bearing rolling, structural resonance, etc.) must be suppressed to the lowest level. This involves low-noise design dimensions such as the optimization of the tooth profile and meshing of the transmission pair.

[0007] Currently, common linear drive mechanisms (such as standard ball screws, rack and pinion gears, and timing belts) each have their limitations: pursuing compactness often sacrifices load-bearing efficiency and rigidity; strengthening the structure leads to increased size and weight; and focusing on noise reduction design may affect transmission response speed and power density. In specific enclosed environments such as vehicle seats, where space, strength, and noise are sharply intertwined, there is a lack of a highly integrated dedicated linear drive solution on the market that can simultaneously optimize and resolve these contradictions.

[0008] Therefore, there is an urgent need in this field for an innovative, compact transmission mechanism that can achieve high power density, high operational reliability, and ultra-low noise level linear motion output within an extremely limited space through a novel structure and transmission layout, in order to meet the comprehensive performance requirements of the aforementioned specific and demanding application environments. Summary of the Invention

[0009] The purpose of this invention is to provide a compact reciprocating kneading transmission mechanism that comprehensively solves the technical problem of achieving efficient, reliable, and quiet transmission in extremely confined spaces such as vehicle seats through a series of innovative structural layouts and transmission designs.

[0010] To achieve the above objectives, the present invention proposes the following technical solution:

[0011] A compact reciprocating kneading transmission mechanism includes a mounting box and further includes: a main drive mechanism comprising a motor, a drive worm gear, a steering transmission component, and a main drive shaft; the drive worm gear is directly driven by the motor; the axis of the drive worm gear is spatially perpendicular to and does not intersect the axis of the main drive shaft, and the main drive shaft is arranged such that its axis extends along the diagonal direction of the mounting box to obtain the maximum effective length of the main drive shaft within the limited space of the mounting box; the steering transmission component is connected between the drive worm gear and the main drive shaft to convert the rotational motion of the drive worm gear into the rotational motion of the main drive shaft; a first output mechanism is driven to the main drive shaft for outputting rotational motion with a first reduction ratio; a second output mechanism is driven to the main drive shaft for outputting rotational motion with a second reduction ratio; wherein the first reduction ratio and the second reduction ratio are different.

[0012] As a preferred embodiment of the present invention, the steering transmission component is a drive worm gear coaxially fixedly sleeved on the main drive shaft, and the drive worm gear meshes with the drive worm.

[0013] In a preferred embodiment of the present invention, the drive worm gear is coaxially and fixedly connected to the output shaft of the motor, forming a direct transmission pair.

[0014] As a preferred embodiment of the present invention, the first output mechanism includes a first worm, a first worm wheel, and a first output shaft; the first worm is coaxially and fixedly disposed with the main drive shaft; the first worm wheel meshes with the first worm; and the first output shaft is fixedly connected to the center of the first worm wheel.

[0015] As a preferred embodiment of the present invention, the first worm gear is configured as an axially extended portion of one end of the main drive shaft, and is an integral structure with the main drive shaft.

[0016] As a preferred embodiment of the present invention, the second output mechanism includes a first transmission pair and a second transmission pair connected in sequence. The power is decelerated or accelerated by the first transmission pair from the main drive shaft, and then output as rotational motion through the second transmission pair.

[0017] As a preferred embodiment of the present invention, the first transmission pair is a gear transmission pair, including a first gear and a second gear that mesh with each other; the first gear is fixed to the main drive shaft and is used to transmit rotational motion to the second gear; the second gear is disposed on the second transmission pair and is used to transmit rotational motion to the second transmission pair.

[0018] As a preferred embodiment of the present invention, the second transmission pair is a worm gear transmission pair, including a second worm and a second worm wheel that mesh with each other; the second worm is disposed beside the main drive shaft, and the second gear is coaxially and fixedly connected to the second worm; a second output shaft is coaxially and fixedly connected to the center of the second worm wheel.

[0019] As a preferred embodiment of the present invention, the mounting box includes a first cover, a second cover, and a box partition; the first cover and the second cover are respectively encapsulated on both sides of the box partition; the box partition is provided with a plurality of mounting slots for accommodating and positioning various transmission components.

[0020] As a preferred embodiment of the present invention, the rotational motion output by the first output mechanism is used to drive the kneading action; the rotational motion output by the second output mechanism is used to drive the reciprocating walking action.

[0021] As can be seen from the above technical solutions, the compact reciprocating kneading transmission mechanism provided by the present invention comprehensively solves the technical problem of achieving efficient, reliable, and quiet transmission in extremely confined spaces such as vehicle seats through a series of innovative structural layouts and transmission designs. Compared with the prior art, the present invention has the following significant beneficial effects.

[0022] (1) It greatly improves the compactness of the transmission mechanism structure and achieves the ultimate minimization of volume and size.

[0023] This invention is not a simple reduction of the traditional transmission scheme, but a systematic reconstruction and optimization of the three-dimensional spatial layout, thereby fundamentally achieving ultimate compactness.

[0024] A three-dimensional collaborative dimensional optimization strategy was implemented: optimal dimensional benchmarks were established for the width, thickness, and length of the mounting box. In the width direction, the outer diameter of the motor was used as the limit. In the thickness direction, a pair of staggered helical gears, consisting of a first gear and a second gear, achieved a specific inter-axis distance and angle through their unique spatial staggered layout. This design enabled a compact layout of the transmission mechanism in the thickness direction, avoiding simple superposition of outer diameter dimensions and effectively reducing thickness. In the length direction, the main drive shaft was arranged along the diagonal of the box, utilizing the longest diagonal distance within the box as the effective shaft length, thereby significantly reducing the box length while maintaining functionality.

[0025] Highly integrated structural design: A one-piece molded housing serves as the unified basic component, and the first worm gear and main drive shaft are designed as a single unit, eliminating additional couplings and connecting structures. This highly integrated design not only reduces the number of parts but also physically compresses the overall size of the mechanism.

[0026] Efficient use of space: The combination of a multi-axis parallel layout (the axes of the drive worm gear, the second output shaft, and the first worm gear are parallel to each other) and a diagonal layout of the main drive shaft makes the power transmission path clear and direct, minimizes the mutual interference of the transmission chain in space, and achieves a high degree of integration in a small space.

[0027] (2) Significantly improved the strength and overall reliability of actuator components.

[0028] While pursuing compactness, the present invention ensures high reliability and long service life of the mechanism in vehicle vibration environment through the following design.

[0029] Enhanced structural rigidity: The integral stamped or injection-molded box partition forms a seamless, rigid base, which enhances structural stability from the source and can effectively resist vibrations and stresses generated during transmission, providing a precise and stable installation foundation for each transmission component.

[0030] Optimization of key transmission connections: The coaxial fixed connection between the motor and the drive worm gear forms a direct rigid transmission pair, eliminating the backlash, slippage and additional stress that may exist in traditional belt or gear transmissions, and improving the reliability of power transmission.

[0031] Precision and stability of the support structure: Key rotating components such as the main drive shaft and the second worm gear are all supported by carefully selected bearings. These bearings are precisely pressed into the precision slots in the housing, which not only ensures smooth rotation but also precisely limits the axial and radial positions of each shaft, ensuring the alignment and stability of the transmission system under long-term operation and vibration environments, and reducing abnormal wear.

[0032] (3) Effectively improves the low noise performance of the actuator transmission method.

[0033] This invention addresses both the generation and propagation of noise, implementing a number of targeted noise reduction measures to achieve ultra-low noise operation.

[0034] Suppressing noise generation at its source: The worm gear pair is selected as the main reduction element, which inherently features smooth meshing and low noise. By precisely designing the pitch or tooth pitch of each worm, the number of threads, and the matching worm gear parameters, the meshing state is optimized, thereby reducing impact and vibration noise during transmission at its source.

[0035] Noise propagation is blocked through structural design: the high-rigidity integrated housing structure effectively suppresses and attenuates vibrations generated by internal transmission components, preventing them from amplifying and resonating to form noise. Meanwhile, the direct drive method (coaxial fixed connection) avoids the meshing squealing that may occur with multi-stage gear transmissions.

[0036] To ensure accuracy and avoid abnormal noise: All transmission pairs are accurately positioned in precision slots in the housing, ensuring excellent transmission alignment and avoiding abnormal wear and collision noise caused by assembly errors or misalignment. This results in extremely low operating noise, fully meeting the stringent requirements for quietness in the vehicle environment.

[0037] In summary, through the above-mentioned systematic and integrated innovative design, this invention successfully achieves a high level of unity between three goals that are traditionally considered contradictory: compactness, reliability, and low noise. It provides a high-performance transmission solution that is particularly suitable for extremely harsh environments such as in-vehicle seat massage systems, and has significant technological advancements and broad industrial application value.

[0038] It should be understood that all combinations of the foregoing concepts and the additional concepts described in more detail below can be considered part of the inventive subject matter of this disclosure, provided that such concepts do not contradict each other.

[0039] The foregoing and other aspects, embodiments, and features of the teachings of the present invention will be more fully understood from the following description in conjunction with the accompanying drawings. Other additional aspects of the invention, such as features and / or beneficial effects of exemplary embodiments, will become apparent from the following description or may be learned through practice of specific embodiments according to the teachings of the present invention. Attached Figure Description

[0040] The accompanying drawings are not drawn to scale. In the drawings, each identical or nearly identical component shown in the various figures may be denoted by the same reference numeral. For clarity, not every component is labeled in each figure. Embodiments of various aspects of the invention will now be described by way of example and with reference to the accompanying drawings.

[0041] Figure 1 This is a top view of the second side of the transmission mechanism according to an embodiment of the present invention.

[0042] Figure 2 This is a top view of the first side of the transmission mechanism according to an embodiment of the present invention.

[0043] Figure 3 This is a side view of the transmission mechanism according to an embodiment of the present invention.

[0044] Figure 4 This is a schematic diagram of the second side axial structure of the transmission mechanism according to an embodiment of the present invention.

[0045] Figure 5 This is a schematic diagram of the first side axial structure of the transmission mechanism according to an embodiment of the present invention.

[0046] Figure 6 This is an exploded structural diagram of the transmission mechanism according to an embodiment of the present invention.

[0047] Figure 7 This is a schematic diagram of the transmission mechanism of this invention after it is encapsulated in the mounting box, according to an embodiment of the present invention.

[0048] Figure 8 This is a top view of the transmission mechanism of an embodiment of the present invention, encapsulated on the second side of the mounting box.

[0049] Figure 9 This is a top view of the transmission mechanism of an embodiment of the present invention, encapsulated on the first side of the mounting box.

[0050] Figure 10 This is a side view of the transmission mechanism of this invention after it is encapsulated in the mounting box, according to an embodiment of the invention.

[0051] The meanings of the reference numerals in the figure are as follows.

[0052] 1. Motor; 2. Drive worm; 3. Drive worm wheel; 4. Main drive shaft; 5. First worm; 6. First worm wheel; 7. First output shaft; 8. First gear; 9. Second gear; 10. Second worm; 11. Second worm wheel; 12. Second output shaft; 13. Mounting box; 1301. First cover; 1302. Second cover; 1303. Box partition. Detailed Implementation

[0053] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of the present invention. All other embodiments obtained by those skilled in the art based on the described embodiments of the present invention without creative effort are within the scope of protection of the present invention. Unless otherwise defined, the technical or scientific terms used herein should have the ordinary meaning understood by those skilled in the art.

[0054] The terms "first," "second," and similar words used in the specification and claims of this patent application do not indicate any order, quantity, or importance, but are merely used to distinguish different components. Similarly, unless the context clearly indicates otherwise, the singular forms of "an," "a," or "the," etc., do not indicate a quantity limitation, but rather indicate the presence of at least one. Terms such as "comprising" or "including" mean that the element or object preceding "comprising" encompasses the features, integrals, steps, operations, elements, and / or components listed following "comprising" or "including," and do not exclude the presence or addition of one or more other features, integrals, steps, operations, elements, components, and / or collections thereof. Terms such as "upper," "lower," "left," and "right" are used only to indicate relative positional relationships; when the absolute position of the described object changes, the relative positional relationship may also change accordingly.

[0055] This invention provides a compact reciprocating kneading transmission mechanism, the core of which is to achieve the output of two independent motion systems driven by a single power source through a highly integrated structural design. The transmission mechanism mainly includes a main drive mechanism, a first output mechanism and a second output mechanism.

[0056] The main drive mechanism, as the core power source, is responsible for the initial conversion and distribution of rotary motion. The first and second output mechanisms, as parallel secondary motion conversion units, receive power from the main drive mechanism and output rotary motion that meets specific functional requirements through different transmission paths and reduction ratios. These three mechanisms are compactly integrated into a volume-optimized mounting box 13, together forming a highly efficient, reliable, and low-noise transmission system.

[0057] In some specific embodiments of the present invention, the first output mechanism and the second output mechanism respectively output rotational motions that meet specific functional requirements. A typical application scenario is massage. For example, the rotational motion output by the first output mechanism realizes a kneading action, and the rotational motion output by the second output mechanism realizes a reciprocating walking action. The two do not interfere with each other and work together to form a reciprocating kneading action to achieve a massage effect.

[0058] Specifically, such as Figures 1 to 5 As shown, the main drive mechanism includes a motor 1, a drive worm 2, a drive worm wheel 3, and a main drive shaft 4. These components are connected together to form the core power transmission chain (main transmission path) of the transmission mechanism. This power transmission chain realizes the direct, compact, and efficient conversion and transmission of power from the motor 1 to the main drive shaft 4, providing the basic power input for the entire mechanism to achieve low-noise and high-reliability reciprocating kneading motion in a limited space.

[0059] In some preferred embodiments of the present invention, the drive worm 2 is coaxially and fixedly connected to the output shaft of the motor 1, thereby forming a direct transmission pair. This allows the torque output by the motor 1 to be directly transmitted to the drive worm 2 via its output shaft without any additional transmission links, and then transmitted from the drive worm 2 to the main drive shaft 4. This helps to simplify the structure, improve transmission efficiency, and reduce potential noise sources. The main drive shaft 4 is located on one side of the drive worm 2, and its axis is spatially perpendicular to and does not intersect with the axis of the drive worm 2. Specifically, the axis of the main drive shaft 4 and the axis of the drive worm 2 do not intersect spatially, and the angle between their projections along the perpendicular direction of the axis of the drive worm 2 and the axis of the drive worm 2 is 90°. Therefore, to achieve power transmission in this arrangement, a drive worm wheel 3 is provided between the drive worm 2 and the main drive shaft 4 to achieve power reversal transmission. Specifically, the drive worm gear 3 is coaxially fixedly sleeved on one end of the main drive shaft 4 near the drive worm 2 and meshes with the drive worm 2. Based on this, the rotational motion of the drive worm 2 will be converted into the rotational motion of the drive worm gear 3, which will then directly drive the main drive shaft 4 to rotate around its own axis.

[0060] Therefore, the transmission process of the main drive mechanism can be summarized as follows: after the motor 1 starts, its output shaft directly drives the drive worm 2 to rotate; the drive worm 2 transmits motion and torque to the drive worm wheel 3 through meshing with the drive worm wheel 3; since the drive worm wheel 3 is coaxially and fixedly connected to the main drive shaft 4, it ultimately drives the main drive shaft 4 to output rotational power. This integrated transmission chain has the characteristics of compact structure, short and direct transmission path, and is very suitable for environments with strict limitations on installation space and operating noise, such as the interior of car seats.

[0061] The main drive mechanism of this invention achieves a single power reversal transmission through a worm gear pair, ensuring that the axial direction of the output shaft of motor 1 is perpendicular to the axial direction of the main drive shaft 4 in space. Compared to the traditional linear transmission layout where motor 1, drive worm 2, and main drive shaft 4 are coaxial, this invention effectively utilizes vertical space, significantly reducing the width of the transmission mechanism along the axial direction of motor 1, thus laying the foundation for a highly compact overall structure in confined installation environments.

[0062] Specifically, such as Figures 1 to 5 As shown, the first output mechanism includes a first worm 5, a first worm wheel 6, and a first output shaft 7. Through the combination and connection of these components, the first output mechanism constitutes a secondary motion conversion unit downstream of the main transmission path. Its function is to further convert the rotational motion input from the main drive shaft 4 into the rotational output of the first worm wheel 6 axis, thereby achieving motion transformation in a specific direction and posture. The force transmission path based on this transmission chain is referred to as the first output path.

[0063] Specifically, the first worm 5 is coaxially fixed to the main drive shaft 4, enabling it to rotate synchronously with the main drive shaft 4; the first worm wheel 6 is arranged on one side of the first worm 5 and meshes with it, thus forming a pair of shaft transmission pairs with spatially intersecting axes; the first output shaft 7 passes through and is fixedly connected to the first worm wheel 6, enabling the first worm wheel 6 to drive the first output shaft 7 to rotate synchronously. Optionally, the first output shaft 7 and the first worm wheel 6 can be connected by a key connection, interference fit, or fastener fixation.

[0064] In some specific embodiments of the present invention, the first worm 5 and the main drive shaft 4 are preferably coaxially fixed. The first worm 5 is constructed as an axial extension of the main drive shaft 4 at the end away from the drive worm wheel 3, that is, a threaded tooth surface is directly machined on the surface of this shaft section, so that the first worm 5 and the main drive shaft 4 become an integrally formed and synchronously rotating component. This not only eliminates the need for additional connecting parts (such as couplings, keys, etc.) between the first worm 5 and the main drive shaft 4, reducing the number of parts and simplifying the assembly process, but also fundamentally eliminates transmission errors, abnormal noises, and wear that may be caused by connection gaps, improving transmission accuracy and smoothness. In addition, as an integral rotating body, this structure avoids the weak links that may exist in segmented connections. The overall rigidity and torque strength are significantly better than the split-combination structure, enabling more reliable torque transmission, especially suitable for environments with vibration or impact. Since there is no need to reserve installation space for the connection part, it helps to further reduce the size of the transmission mechanism in the axial direction of the main drive shaft, contributing to the realization of an extremely compact overall layout. The one-piece molded structure is easier to perform dynamic balancing correction, which can fundamentally reduce vibration and noise during high-speed rotation caused by uneven mass distribution, meeting the design goal of low-noise operation.

[0065] Therefore, the power transmission process of the first output mechanism can be simply described as follows: when the main drive shaft 4 rotates, it directly drives the first worm gear 5, which is integrated with it, to rotate synchronously. The first worm gear 5 transmits motion to the first worm wheel 6 through meshing with the first worm wheel 6. The first worm wheel 6 then drives the first output shaft 7, which is fixed to it, and finally outputs rotational motion around the axis of the first output shaft 7. This design eliminates additional couplings or connecting links, greatly improving the integration, rigidity, and reliability of the transmission chain, while reducing vibration and noise that may be caused by accumulated assembly errors.

[0066] Specifically, such as Figures 1 to 5 As shown, the second output mechanism includes a first gear 8, a second gear 9, a second worm 10, a second worm wheel 11, and a second output shaft 12. This second output mechanism is parallel to the aforementioned first output mechanism and serves as another secondary motion conversion unit downstream of the main drive shaft 4. Its function is to convert the rotational motion of the main drive shaft 4 into the rotational motion of the second output shaft through two stages of speed change and reversal between gears and between worm wheels and worms, thereby driving the execution module to move along a predetermined trajectory.

[0067] Specifically, the first gear 8 is fixedly sleeved on the main drive shaft 4 and located at the connection between the main drive shaft 4 and the first worm 5; the second worm 10 is arranged beside the main drive shaft 4, and the second worm 10 and the main drive shaft 4 are spatially staggered but do not intersect, forming a set spatial angle between them. In some preferred embodiments, the spatial angle between the second worm 10 and the main drive shaft 4 on the horizontal projection plane is 5° to 45°, so as to realize the conversion of the power direction. The second gear 9 is fixedly installed on the end of the second worm 10 near the first gear 8 so that it meshes with the first gear 8, thereby forming a first-stage gear transmission pair; the second worm wheel 11 is arranged beside the second worm 10 and meshes with the second worm 10 to form a second-stage worm transmission pair; the second output shaft 12 is coaxially fixedly sleeved on the second worm wheel 11 and rotates synchronously with it. Optionally, the second output shaft 12 and the second worm wheel 11 can be connected by key connection, interference fit or fastener fixation.

[0068] In some preferred embodiments of the present invention, such as Figure 1 , Figure 2 , Figure 3 and Figure 5 As shown, preferably, the first gear 8 is a conventional spur gear, while the second gear 9 is a helical variable thickness gear. This gear has a helical tooth profile, and the tooth thickness decreases from the tooth root to the tooth tip. The gear pair formed by the meshing of the second gear 9 and the first gear 8 achieves a specific shaft spacing and shaft angle by utilizing the spatial configurability of the helical teeth without sacrificing the meshing strength. This enables the transmission mechanism to achieve a compact layout in the thickness direction and effectively reduces the overall profile size of the transmission mechanism.

[0069] Therefore, the power transmission process of the second output mechanism can be summarized as follows: when the main drive shaft 4 rotates, it drives the first gear 8 to rotate synchronously; the first gear 8, through meshing with the second gear 9, transmits power to the second worm 10; the second worm 10 drives the second worm wheel 11 meshing with it, ultimately driving the second output shaft 12 to output rotational motion around its axis. This design, through combinations of gears, gears and worms, and worms and worm wheels, achieves a high reduction ratio transmission within a limited space, while also considering transmission smoothness and structural compactness. The power transmission path based on this transmission chain is called the second output path.

[0070] In this transmission mechanism, the axes of the drive worm 2, the second output shaft 12, and the first worm wheel 6 are spatially parallel. This spatially parallel axis layout greatly optimizes the structural compactness and assembly rationality of the transmission mechanism within a confined space. It realizes two parallel output paths branching from the same main shaft but possessing completely different transmission characteristics, with no motion interference between all components. This design, which achieves "one source, two paths, differentiated outputs" efficiently and reliably under extreme space constraints through the coordinated optimization of three-dimensional spatial layout and transmission parameters, is precisely the significant technological advancement and practical value of this invention compared to traditional general transmission layouts or simple parallel dual-motor solutions. It perfectly meets the stringent requirements for integration, performance, and reliability in narrow installation environments (such as vehicle seats).

[0071] In some specific embodiments of the present invention, such as Figures 6 to 9 As shown, in order to compactly integrate the above-mentioned multiple transmission components (such as motor 1, worm gear, worm wheel, etc.) and ensure the accuracy and stability of their relative positions, the transmission mechanism also includes a mounting box 13.

[0072] The mounting box 13 mainly includes a first cover 1301, a second cover 1302, and a core box partition 1303. The box partition 1303 has a rectangular parallelepiped structure with opposing first and second sides, both of which are open. The first cover 1301 and the second cover 1302 are detachably sealed to the first and second sides of the box partition 1303, respectively, forming a closed box structure to provide support, positioning, and protection for the internal transmission components. The first cover 1301 and the second cover 1302 are detachably sealed, optionally using screws for connection.

[0073] The housing partition 1303 of this invention is preferably manufactured using a one-piece molding process, such as metal stamping or engineering plastic injection molding. This manufacturing method ensures that the housing partition 1303 itself is a seamless integral component, thereby significantly enhancing its overall structural rigidity and stability from the source. It can effectively resist the vibration and stress generated during transmission and provide a precise and stable installation foundation for each transmission component.

[0074] As an example of optimization, to orderly accommodate the various components, multiple precisely positioned mounting slots are provided on both sides of the housing partition 1303. On its first side, from the first end (i.e., the end closest to where the motor 1 is installed) to the second end, there are sequentially provided: a motor slot for accommodating the motor 1, a second rod slot for installing the second worm gear 10, a third wheel slot for accommodating the second worm wheel 11, and a through slot that runs through both sides of the housing partition 1303. On the second side of the housing partition 1303, from the first end to the second end, there are sequentially provided: a first wheel slot for accommodating the drive worm wheel 3, a first rod slot for installing the main drive shaft 4, the through slot (running through both sides), and a second wheel slot for accommodating the first worm wheel 6.

[0075] It is worth noting that the center of the motor slot, the second wheel slot and the third wheel slot are all provided with through holes that pass through the housing partition 1303. These through holes are used for the output shaft of the power supply 1, the first output shaft 7 and the second output shaft 12 to pass through, so that they can pass through the housing partition 1303. For example, the first output shaft 7 and the second output shaft 12 will also extend out of the housing so as to connect with external actuators (such as the kneading swing arm or walking module of the massage mechanism).

[0076] In this embodiment of the invention, the first wheel groove, the first rod groove, and the through groove are coaxially connected, with their axes extending from one apex of the first end of the housing partition 1303 to the opposite apex of the second end. This means that the main drive shaft is approximately arranged along the diagonal direction of the housing partition 1303, such that the angle between the axis of the main drive shaft 4 and the central axis of the housing partition 1303 in the length-width plane (XY plane) is 5° to 45°. The core advantage of this layout is that, within the limited cuboid space, the longest diagonal distance is effectively utilized as the working length of the main drive shaft 4, providing ample space for arranging multiple transmission elements (such as the drive worm gear 3, the first gear 8, and the first worm 5), which is key to achieving high integration.

[0077] To make the installation positions of each component on the partition 1303 of the enclosure clearer, the installation relationship, position and function of each component are described in detail below.

[0078] Motor 1 is positioned within the motor slot on the first side. A shaft hole is located in the center of the motor slot, through which the output shaft of motor 1 passes. Screw holes are pre-drilled around the perimeter of the motor slot to engage with fixing plates on the motor 1 housing. The motor 1 is securely fixed via detachable connections such as bolts, ensuring stable power input.

[0079] Preferably, in some specific embodiments of the present invention, the mounting box 13 is not designed to house the entire body of the motor 1 within its internal cavity. Instead, only the motor end, where the output shaft of the motor 1 is located, is inserted into the motor slot on the partition of the box and fixed with bearings. Correspondingly, the remaining main body of the motor 1 (including the tail section of the housing and the heat dissipation structure, etc.) is reasonably exposed in the external space of the mounting box 13. This design not only significantly reduces the overall size of the transmission mechanism in the thickness direction of the mounting box, but also facilitates the heat dissipation and maintenance of the motor 1, and is one of the measures to achieve a compact overall structure.

[0080] The two ends of the main drive shaft 4 (on which the drive worm gear 3, the first gear 8, etc. are integrated or fixed) are rotatably supported on the two end side walls of the first rod groove on the second side by a pair of first bearings. This bearing support structure allows the main drive shaft 4 to rotate freely along its axis, while the bearings precisely define its position, ensuring the stability of its meshing with the drive worm gear 2. After installation, the drive worm gear 3 is located in the first gear groove, and the first gear 8 is aligned with the through groove position, creating conditions for its meshing with the second gear 9.

[0081] The second worm gear 10 is rotatably mounted on the sidewalls of the second groove on the first side via a pair of second bearings to achieve stable rotation. The second gear 9, fixed thereon, is also aligned with the through groove and meshes with the first gear 8 on the main drive shaft 4 through the through groove.

[0082] The second worm gear 11 is housed in the third gear groove and meshes with the second worm 10. This arrangement allows power to be efficiently transmitted from the main drive shaft 4 to the second worm gear 11.

[0083] The first worm gear 6 is housed in the second groove on the second side. Since the main drive shaft 4 adopts a diagonal layout, the installation positions of its two ends (i.e., the end of the drive worm gear 3 and the end of the first worm 5) are located in the two diagonal corner areas of the housing 1303, which makes the first worm gear 6 and the motor 1 spatially diagonally distributed, maximizing the use of the effective space inside the housing and avoiding interference between components.

[0084] Among them, the output shaft of motor 1, the second output shaft 12, the first output shaft 7 and other shafts are all fixedly installed on their corresponding components by their matching bearing sleeves, which is existing technology and will not be described in detail here.

[0085] Finally, after all components are precisely installed and positioned, the first cover 1301 and the second cover 1302 are respectively placed on both sides of the housing partition 1303 and tightened to complete the encapsulation of the entire transmission mechanism. The second output shaft 12 and the first output shaft 7 will pass through the mounting housing 13 to connect with external actuators (such as massage kneading components).

[0086] In this installation layout, the rotation axis of the drive worm gear 3, the rotation axis of the first gear 8 (i.e., the axis of the main drive shaft 4), and the axis of the second worm 10 are parallel; simultaneously, the axis of the first worm gear 6 and the axis of the second worm gear 11 are also parallel to each other. This multi-axis parallel layout design, combined with the diagonal arrangement of the main drive shaft 4, minimizes the mutual interference of the transmission chain in space, making the power transmission path clear and direct. This is one of the core geometric constraints for achieving highly integrated transmission in such a confined space.

[0087] To achieve ultimate compactness in three-dimensional space, the mounting box 13 follows a targeted optimization strategy in determining its external dimensions.

[0088] like Figure 1 , Figure 2 , Figure 4 , Figure 5 and Figures 8 to 9 As shown, in the width direction (X direction), the dimensions of the mounting box 13 are primarily designed based on the maximum outer diameter of the motor 1 housing. The width of the box partition 1303 is preferably set to just accommodate the motor slot, which fundamentally minimizes the dimensions of the mounting box 13 in this direction. Of course, within reasonable design limits, the width of the box partition 1303 can be appropriately increased to allow space for screw holes, clips, etc.

[0089] like Figure 10 As shown, in the thickness direction (Z-direction), the dimensions of the mounting box 13 must be able to accommodate the axial projections of all worm gears, worm shafts, and gear pairs. The meshing of the first gear 8 and the second gear 9 forms a pair of staggered-axis helical gears. Their unique spatial staggered layout achieves specific inter-axis distances and angles, enabling a compact layout of the transmission mechanism in the thickness direction and avoiding the thickness accumulation resulting from simply adding the outer diameters of the two gears. Therefore, the total thickness of the mounting box 13 is mainly determined by the larger of the outer diameter of the drive worm gear 3 and the optimized total meshing thickness of the gears, achieving a reduction in size in this direction.

[0090] like Figure 8 and Figure 9As shown, in the longitudinal direction (Y direction), the dimensions of the mounting box 13 are optimized by arranging the main drive shaft 4 obliquely along the diagonal direction of the box's central spacer 1303. If the main drive shaft 4 were arranged parallel to the side of the box, a larger box length would be required to achieve the same shaft length for arranging the transmission elements. The diagonal layout of this invention effectively utilizes the longest diagonal distance within the box, minimizing the longitudinal dimension of the mounting box 13 while ensuring the necessary shaft length.

[0091] In summary, this invention systematically solves the multidimensional size contradictions faced in integrating complex transmission functions under extreme space constraints through the aforementioned coordinated and targeted design strategies in the three dimensions of width, thickness, and length, ultimately achieving an extremely compact transmission mechanism in terms of overall volume.

[0092] In summary, the design of the mounting box 13, through precise slot planning in the box's central partition and innovative diagonal layout of the main drive shaft 4, successfully integrates a complex multi-stage transmission system into an extremely compact space. This not only achieves precise transmission coordination between components but also enhances the rigidity of the mechanism through the overall box structure, which helps suppress vibration and noise, ultimately perfectly meeting the stringent requirements for space, reliability, and quietness.

[0093] In highly integrated transmission mechanisms, enabling a single motor 1 to simultaneously drive two peer motion mechanisms (e.g., the walking mechanism and kneading mechanism of a massage device) with different output torque requirements is a significant technical challenge in the field. The output shafts of these two mechanisms (the second output shaft 12 and the first output shaft 7) require different final torques. This necessitates that two transmission paths (the second output path and the first output path) branching from the same power source (the main drive shaft) must utilize combinations of transmission pairs of different stages, types, and parameters to produce differentiated overall reduction ratios, thereby achieving their respective required torque and speed at the output end.

[0094] The innovative layout and structural design of this invention, especially the arrangement of the main drive shaft 4 along the diagonal of the housing at interval 1303, provides a key spatial basis for the optimized design of core transmission components (such as worms with different pitches and worm wheels with corresponding helix angles and thicknesses), making it possible to achieve two independent and efficient transmission paths with specific reduction ratios within an extremely compact volume.

[0095] Example 1

[0096] This embodiment provides a specific implementation scheme for a compact transmission mechanism for an automotive seat massager. To achieve differentiated transmission for kneading and walking functions, the core geometric parameters of each key transmission component have been optimized and are summarized in Table 1. The parameters of each key transmission component of the transmission mechanism are the design basis for achieving subsequent differentiated transmission and space compactness.

[0097] Table 1. Core parameters of key transmission components in Example 1

[0098] Parameter name Drive worm gear First worm gear First worm gear First gear Second gear Second worm gear Second worm gear Normal module (mm) 0.65 1.4 1.4 0.9 0.9 0.7 0.7 Number of teeth 34 2 14 16 24 2 28 Rotation right Left Left / right Left Left Pitch circle diameter (mm) 22.694 10.158 20.242 14.4 22.519 4.0933 20.2176 Pitch circle helix angle (°) 13.1356 / 14.4641 / 16.4273 / 14.198 Pitch circle lead angle (°) / 16 / / / 20 /

[0099] In this embodiment, based on the precise parameter configuration in Table 1, where the first output mechanism corresponds to the kneading mechanism of the massage device and the second output mechanism corresponds to the walking mechanism of the massage device, their reduction ratios are configured as follows, which provides a clear and verifiable technical solution for how the present invention achieves the above-mentioned differentiated transmission.

[0100] The design goal of the reduction ratio difference is to achieve a reduction ratio of approximately 1:3 between the kneading path and the walking path through the gear ratio arrangement, thereby optimizing space utilization under a single motor drive. Although the walking path, as a branch of the main drive shaft 4, has a large reduction ratio, the torque of the branch motor 1 is relatively small, which helps to balance the overall transmission load.

[0101] The specific design and application relationships of each transmission path are as follows.

[0102] For the kneading transmission path: its power is transmitted sequentially through two stages of worm gear-worm wheel pair.

[0103] The first stage of the transmission pair consists of a driving worm 2 and a driving worm wheel 3. Assuming the number of threads (i.e., the number of threads) of the driving worm 2 is 2 and the number of teeth of the driving worm wheel 3 is 34, then the reduction ratio for this stage is i1 = 34 / 2 = 17.

[0104] The second-stage transmission pair consists of a first worm 5 and a first worm wheel 6. Assuming the first worm 5 has 2 threads and the first worm wheel 6 has 14 teeth, the reduction ratio for this stage is i2 = 14 / 2 = 7.

[0105] Therefore, the total reduction ratio i of the kneading transmission path 揉捏 =i1×i2=17×7=119. This reduction ratio design enables the first output shaft 7 (kneading shaft) to output a relatively high speed and moderate torque rotational motion that meets the requirements of its massage action.

[0106] For the walking transmission path: its power is transmitted sequentially through a first-stage gear pair and a first-stage worm-worm wheel pair.

[0107] The first-stage transmission pair shares the driving worm 2 and driving worm wheel 3 with the kneading path, and the reduction ratio is also i1=17.

[0108] The second-stage transmission pair consists of the first gear 8 and the second gear 9. Assuming the first gear 8 has 16 teeth and the second gear 9 has 24 teeth, the reduction ratio of this gear pair is i2′ = 24 / 16 = 1.5. This is the speed increase, but from a system perspective, its reciprocal relationship is usually included in the total reduction chain.

[0109] The third-stage transmission pair consists of the second worm 10 and the second worm wheel 11. Assuming the second worm 10 has 2 threads and the second worm wheel 11 has 28 teeth, the reduction ratio for this stage is i3 = 28 / 2 = 14.

[0110] Therefore, the total reduction ratio i of the walking transmission path 行走 =i1×i2′×i3=17×1.5×14=357.

[0111] The reduction ratio of kneading to walking is approximately 119:357≈1:3, which reflects the high reduction ratio design achieved through branch paths. Although the reduction ratio of the walking path is large, the torque of the branch walking motor 1 is small, which is conducive to achieving efficient power distribution in a compact space.

[0112] The compact design of this invention is ultimately reflected in the extremely small size of the mounting box 13. For example... Figures 1 to 3 As shown, the axis of the main drive shaft 4 and the central axis of the housing 1303 form a 12.5° angle in the length-width plane (XY plane), and the axis of the main drive shaft 4 and the second worm gear 10 form a 20° angle in the horizontal projection plane. By precisely controlling the relative positions between the axes, the core transmission components are successfully guided to be staggered along the diagonal direction of the housing in three-dimensional space, thereby converting corner spaces that are difficult to utilize under traditional parallel or vertical layouts into effective installation and transmission areas. Figures 8 to 10 As shown, the encapsulated overall mechanism has a maximum width (X-direction) of only 38.3±0.3mm and a minimum width of 34.9±0.3mm; a length (Y-direction) of 110.2±0.3mm; and a maximum thickness (Z-direction) of only 45±0.3mm and a minimum thickness of 42.3±0.3mm. This extremely reduced size directly verifies that through diagonal layout and differentiated parameter design, the limited space was successfully utilized efficiently in both the radial and axial directions. This provides sufficient axial length for worm gears with different pitches or tooth pitches, and provides reasonable diameter and thickness design space for the worm wheel. Thus, the miniaturization of the entire mechanism was achieved while ensuring the strength and efficiency of each transmission pair.

[0113] Through the specific and differentiated multi-stage transmission pair design of Embodiment 1 above, and by making full use of the axial space and radial clearance created by the diagonal layout, the present invention successfully provides sufficient axial arrangement length for worms with different pitches or tooth pitches (e.g., drive worm 2, first worm 5, second worm 10) within the same extremely narrow mounting box 13, enabling them to optimize the thread lead and number of starts according to their respective reduction ratio requirements; and provides reasonable diameter and thickness design space for the meshing worm wheels (e.g., drive worm wheel 3, first worm wheel 6, second worm wheel 11) to match the helix angle of different worms and ensure sufficient tooth surface contact strength and transmission efficiency.

[0114] The transmission mechanism described in this invention is universal, but it is particularly suitable for in-vehicle seat massage systems with extreme requirements for space, performance, and noise. As is well known, the application scenarios of in-vehicle seat massage systems are fundamentally different from those of traditional home massage chairs, specifically manifested in three core contradictions: limited installation space and height; the need to output massage force no less than that of home products in a smaller volume; and the requirement to suppress operating noise to an extremely low level to ensure driving safety and passenger comfort.

[0115] The transmission mechanism of this invention systematically solves the above-mentioned contradictions through the following innovative design, and achieves high-performance integration in the vehicle environment.

[0116] (1) Diagonal layout is adopted. By innovatively arranging the main drive shaft 4 in the diagonal direction of the housing 1303, the longest axial dimension in the finite cuboid space is maximized, providing a physical basis for accommodating multi-stage transmission pairs, which is the key to realizing the integration of complex functions in a very small volume.

[0117] (2) Highly integrated one-piece structure. The one-piece molded box partition 1303 is used as the mounting base for all transmission components, and the first worm gear 5 and the main drive shaft 4 are designed as one-piece components, eliminating unnecessary connecting parts and assembly space, realizing the minimal physical integration of the transmission chain, and making the overall module extremely compact in length, width and height.

[0118] (3) Differentiated multi-stage reduction design. By independently configuring transmission pairs with different reduction ratios for the kneading and walking output paths (for example, the reduction ratio of the kneading path to the walking path is 1:3), it is ensured that two completely different torque-speed characteristics can be output simultaneously from the same power source. This allows the second output shaft 12 to output the torque required to drive the entire mechanism to move smoothly, while the first output shaft 7 can also output the appropriate torque and speed suitable for the massage action, thus ensuring that the core massage force and effect are not diminished while the overall size is greatly reduced.

[0119] (4) Transmission optimization and enhanced stability. The worm gear pair is used as the main reduction element, which has the characteristics of smooth meshing and low noise. By precisely designing the pitch or tooth pitch, number of threads and matching worm gear parameters of each worm, the meshing state is optimized and the impact and vibration are reduced. At the same time, the integrated high-rigidity housing structure effectively suppresses resonance, reducing mechanical noise from both the source and the propagation path.

[0120] (5) Direct drive and high-precision positioning. The coaxial fixed connection between motor 1 and drive worm gear 2 eliminates the meshing noise and gap noise of traditional belt or gear transmission. All bearings and transmission pairs are accurately positioned in the precision slots of the housing at interval 1303, ensuring transmission alignment and avoiding abnormal wear and noise caused by misalignment, so that the overall operating sound meets the stringent requirements of vehicle environment for quietness.

[0121] In summary, this transmission mechanism is not simply a miniaturization of existing general transmission components, but a systematic and integrated innovative design addressing the three major contradictions of space, torque, and noise in the specific application scenario of in-vehicle seat massage. It successfully achieves efficient, reliable, and quiet power distribution and output in an extremely compact space, fundamentally meeting the higher requirements of in-vehicle integrated mechanical massage systems for transmission mechanisms, and possesses high adaptability to various scenarios and advanced technology.

[0122] While the present invention has been disclosed above with reference to preferred embodiments, it is not intended to limit the invention. Those skilled in the art can make various modifications and refinements without departing from the spirit and scope of the invention. Therefore, the scope of protection of the present invention shall be determined by the claims.

Claims

1. A compact reciprocating kneading transmission mechanism, comprising a mounting box (13), characterized in that, Also includes: The main drive mechanism includes a motor (1), a drive worm (2), a steering transmission component, and a main drive shaft (4); the drive worm (2) is directly driven by the motor (1); the axis of the drive worm (2) is spatially perpendicular to and does not intersect the axis of the main drive shaft (4), and the main drive shaft (4) is arranged such that its axis extends along the diagonal direction of the mounting box (13) so that the main drive shaft (4) obtains the maximum effective length within the limited space of the mounting box (13); the steering transmission component is connected between the drive worm (2) and the main drive shaft (4) for converting the rotational motion of the drive worm (2) into the rotational motion of the main drive shaft (4); The first output mechanism is connected to the main drive shaft (4) and is used to output rotational motion with a first reduction ratio; The second output mechanism is connected to the main drive shaft (4) and is used to output rotational motion with a second reduction ratio; The first reduction ratio is different from the second reduction ratio.

2. The compact reciprocating kneading transmission mechanism according to claim 1, characterized in that, The steering transmission component is a drive worm wheel (3) coaxially fixedly sleeved on the main drive shaft (4), and the drive worm wheel (3) meshes with the drive worm (2).

3. The compact reciprocating kneading transmission mechanism according to claim 1, characterized in that, The drive worm (2) is coaxially and fixedly connected to the output shaft of the motor (1), forming a direct transmission pair.

4. The compact reciprocating kneading transmission mechanism according to claim 1, characterized in that, The first output mechanism includes a first worm (5), a first worm wheel (6), and a first output shaft (7); The first worm gear (5) is coaxially fixed with the main drive shaft (4); The first worm gear (6) meshes with the first worm (5); The first output shaft (7) is fixedly connected to the center of the first worm gear (6).

5. The compact reciprocating kneading transmission mechanism according to claim 4, characterized in that, The first worm (5) is constructed as an axial extension of one end of the main drive shaft (4) and is an integral part of the main drive shaft (4).

6. The compact reciprocating kneading transmission mechanism according to claim 4, characterized in that, The second output mechanism includes a first transmission pair and a second transmission pair connected in sequence. The power is generated from the main drive shaft (4), which is decelerated or accelerated by the first transmission pair, and then outputs rotational motion through the second transmission pair.

7. The compact reciprocating kneading transmission mechanism according to claim 6, characterized in that, The first transmission pair is a gear transmission pair, including a first gear (8) and a second gear (9) that mesh with each other; The first gear (8) is fixed to the main drive shaft (4) and is used to transmit rotational motion to the second gear (9); The second gear (9) is disposed on the second transmission pair and is used to transmit rotational motion to the second transmission pair.

8. The compact reciprocating kneading transmission mechanism according to claim 7, characterized in that, The second transmission pair is a worm gear transmission pair, including a second worm (10) and a second worm wheel (11) that mesh with each other. The second worm (10) is located on the side of the main drive shaft (4), and the second gear (9) is coaxially fixedly connected to the second worm (10); The second worm gear (11) is coaxially fixedly connected to a second output shaft (12).

9. The compact reciprocating kneading transmission mechanism according to claim 8, characterized in that, The mounting box (13) includes a first cover (1301), a second cover (1302), and a box partition (1303); The first cover (1301) and the second cover (1302) are respectively encapsulated on both sides of the box partition (1303); The housing partition (1303) is provided with multiple mounting slots for accommodating and positioning various transmission components.

10. The compact reciprocating kneading transmission mechanism according to any one of claims 1-9, characterized in that, The rotational motion output by the first output mechanism is used to drive the kneading action; The rotational motion output by the second output mechanism is used to drive the reciprocating walking motion.

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