Linear drive mechanism and shaver

Abstract

The present application relates to the technical field of hair trimming device, and particularly relates to a linear driving mechanism and a shaver, which comprises: a swing arm for mounting a moving cutter head, the swing arm being arranged on the outer side of a motor along the radial direction of the motor; a motor, an eccentric shaft being mounted on the output shaft of the motor, the eccentric shaft being arranged in parallel with the output shaft; a transmission sheet being arranged at the axial end of the motor, one end of the transmission sheet being rotatably connected with the eccentric shaft, and the other end of the transmission sheet being rotatably connected with the swing arm, so as to convert the circular motion of the eccentric shaft around the output shaft into the reciprocating linear motion of the swing arm along a first direction; and an elastic supporting sheet being mounted between the swing arm and the motor, the elastic supporting sheet providing the swing arm with an elastic reset force along the first direction; the elastic supporting sheet is in a sheet structure, the sheet plane of the elastic supporting sheet is parallel with the axial direction of the output shaft, and the first direction is perpendicular to the sheet plane, so that the problem of relatively large wear and noise of the existing driving mechanism is solved.

Description

Technical Field

[0001] This invention relates to the field of hair trimming equipment technology, and particularly to a linear drive mechanism and a razor. Background Technology

[0002] In existing reciprocating shaver drive mechanisms, the mechanism for linear reciprocating drive of the shaver head uses a motor to drive the output shaft to rotate. The output shaft drives the eccentric shaft to perform circumferential motion. The moving shaver head is mounted on the moving shaver holder, and a guide groove is provided on the shaver head holder. When the eccentric shaft moves in circumferential motion, it slides in the guide groove, thereby driving the moving shaver holder to reciprocate in a predetermined direction, thus achieving the purpose of linear reciprocating drive of the moving shaver head.

[0003] However, this structure has a drawback: the transmission mechanism experiences relatively high wear and noise during operation. Summary of the Invention

[0004] In order to solve the above-mentioned technical problems, the purpose of this invention is to provide a linear drive mechanism that solves the problems of wear and relatively high noise in existing drive mechanisms.

[0005] To achieve the above objectives, the technical solution adopted by the present invention is: a linear drive mechanism, comprising:

[0006] The swing arm is used to mount the moving cutter head. The swing arm is located on the outside of the motor along the radial direction of the motor.

[0007] The motor has an eccentric shaft mounted on its output shaft, and the eccentric shaft is arranged parallel to the output shaft.

[0008] The transmission plate is located at the axial end of the motor. One end of the plate is rotatably connected to the eccentric shaft, and the other end is rotatably connected to the swing arm, so as to convert the circumferential motion of the eccentric shaft around the output shaft into the reciprocating linear motion of the swing arm along the first direction.

[0009] An elastic support plate is installed between the swing arm and the motor to provide the swing arm with an elastic restoring force along the first direction. The elastic support plate is a sheet-like structure, and the plane in which the sheet is located is parallel to the axial direction of the output shaft and perpendicular to the first direction.

[0010] Furthermore, the axis of the output shaft is taken as the x-axis, the first direction is taken as the Y-axis, and the direction that is perpendicular to both the x-axis and the Y-axis is taken as the Z-axis.

[0011] The transmission plate is provided with an elastic deformation zone, which is configured to allow the two ends of the transmission plate to generate elastic relative displacement in the x-axis direction and / or the Z-axis direction.

[0012] By adopting the above technical solution, the technical problem solved by elastic deformation in the X-axis direction is:

[0013] In the actual assembly process of the transmission mechanism, one end of the transmission plate is rotatably connected to the eccentric shaft, and the other end is rotatably connected to the swing arm. The rotatable connection between the two ends involves the assembly and mating of multiple parts. Since the eccentric shaft is mounted on the motor output shaft, the rotor assembly, stator assembly, and output shaft itself inside the motor have manufacturing tolerances. The installation of the swing arm also has dimensional and assembly tolerances. After these tolerances accumulate over multiple stages, the rotatable connection points at both ends of the transmission plate cannot be completely aligned in the X-axis direction. That is, the actual positions of the two connection points deviate axially from the output shaft. When the transmission plate is a completely rigid structure, this axial deviation will generate additional axial stress at the rotatable connection points at both ends, resulting in poor rotation, jamming, and significant operating noise.

[0014] This application provides an elastic deformation zone on the transmission plate that can generate elastic relative displacement in the X-axis direction. When there is an assembly deviation in the X-axis direction at the rotating connection points at both ends of the transmission plate, the elastic deformation zone can absorb the deviation through its own elastic deformation in the X-axis direction, so that the rotating connection points at both ends can rotate normally without axial stress, avoiding jamming and noise caused by assembly tolerances, and ensuring smooth and stable transmission.

[0015] Technical problems solved by elastic deformation in the Z-axis direction:

[0016] During the operation of the transmission mechanism, the eccentric shaft revolves around the output shaft, driving the swing arm to reciprocate along the first direction via the transmission plate. When the swing arm moves to the limit position of the reciprocating stroke in the Y direction, the direction of motion of the eccentric shaft is about to reverse. At this time, the transmission plate needs to apply a reverse pulling force to the swing arm to reverse its direction. Since the swing arm and the moving cutter head mounted on it have a certain inertia, at the moment of reversal, the inertial force will generate an impact load on the rotating connection at both ends of the transmission plate, causing vibration and noise. Long-term operation will also accelerate the wear of the rotating connection and shorten its service life.

[0017] This application provides an elastic deformation zone on the transmission plate that can generate elastic relative displacement in the Z-axis direction. When the swing arm moves to the limit position and generates a reversing impact, the elastic deformation zone can absorb the impact energy through its own elastic deformation in the Z-axis direction, thereby playing a buffering and shock-absorbing role. This protects the rotating connection at both ends of the transmission plate from rigid impact, reduces vibration and operating noise, and extends the service life of the transmission mechanism.

[0018] Synergistic effect of elastic deformation along the X and Z axes:

[0019] It is worth emphasizing that the elastic deformation in the X-axis and Z-axis directions are not two simple, independent functions; there is a significant synergistic effect between them. In actual working conditions, axial deviation caused by assembly tolerances and vertical vibration caused by reversing impacts often coexist and exacerbate each other: axial deviations worsen the stress state at the rotating joints at both ends, making it easier to generate non-axial yaw moments under reversing impacts, further amplifying vibrations and noise; while the vibrations generated by reversing impacts accelerate localized wear caused by assembly deviations, forming a vicious cycle.

[0020] This application, by simultaneously setting elastic deformation zones in both the X-axis and Z-axis directions on the transmission plate, transforms the transmission plate into a "flexible transmission plate" with flexible deformation capabilities in two orthogonal directions in space. This simultaneously resolves the two mutually reinforcing problems of assembly deviation and motion impact: the elastic deformation in the X-axis direction absorbs axial assembly deviation, keeping the rotating connection points at both ends in a normal working posture, thereby reducing the additional yaw torque caused by posture deviation during reversal; the elastic deformation in the Z-axis direction absorbs reversal impact energy, preventing the impact load from being transmitted to the assembly deviation point through rigid connection, avoiding stress concentration and accelerated wear at the deviation point. The combined effect of these two factors fundamentally breaks the vicious cycle of "assembly deviation—impact amplification—wear acceleration," achieving a comprehensive vibration reduction, noise reduction, and service life extension effect greater than the sum of its parts—something that existing technologies cannot achieve by only addressing deviation in one direction or providing buffering in only one direction.

[0021] Furthermore, the elastic deformation zone includes a thickness reduction section disposed on the transmission plate, through which the transmission plate generates elastic displacement in the x-axis direction and / or Z-axis direction.

[0022] By adopting the above technical solution, the elastic deformation zone is the thickness reduction section on the transmission plate. The elastic deformation function can be achieved by local thinning. The processing is simple and does not require additional parts or material changes. Under the premise of ensuring the strength of the main structure of the transmission plate, the flexible deformation capability in a specific direction is achieved.

[0023] Furthermore, the elastic modulus of the elastic deformation zone is lower than that of other parts of the transmission plate.

[0024] By adopting the above technical solution, the elastic deformation zone is composed of a material with an elastic modulus lower than that of the adjacent parts of the transmission plate, and can be formed by two-color injection molding, insert injection molding, etc. Compared with the structural thinning method, the material difference method can make the overall thickness of the transmission plate consistent, the appearance more regular, and the material properties of the elastic deformation zone can be selected independently as needed, resulting in greater design flexibility.

[0025] Furthermore, the transmission plate includes an inner rod extending along the Y-axis and an outer rod disposed on the upper and / or lower side of the inner rod. One end of the outer rod is bent to connect with one end of the inner rod, the other end of the outer rod is rotatably connected to the swing arm, and the other end of the inner rod is rotatably connected to the eccentric shaft.

[0026] The elastic deformation zone includes a first thinning section on the outer rod with reduced thickness along the Z-axis direction, and a second thinning section on the inner rod with reduced thickness along the x-axis direction.

[0027] By adopting the above technical solution, the outer rod is set on the upper side, lower side, or both sides of the inner rod. This facilitates the arrangement of two thinning sections without interference. The two thinning sections are set on different components, each solving the elastic deformation requirements in different directions. The functional division is clear and the structure is compact.

[0028] Furthermore, the transmission plate is a linear plate structure, with its two ends rotatably connected to the eccentric shaft and the swing arm, respectively. The middle part is provided with a first thinning section with thickness reduction along the Z-axis direction and a second thinning section with thickness reduction along the x-axis direction.

[0029] By adopting the above technical solutions, linear sheet structures are the simplest to process, and can be formed in one step by stamping or injection molding, resulting in low manufacturing costs and making them suitable for cost-sensitive product solutions.

[0030] Furthermore, there are two swing arms, which are arranged side by side on the outside of the motor along the motor axis. Both ends of the motor axis are equipped with eccentric shafts and transmission plates. The eccentric shafts are connected to the corresponding swing arms through the transmission plates.

[0031] By adopting the above technical solution, the double swing arms can drive two sets of moving cutter heads respectively, realize the synchronous operation of multiple cutter heads, improve the shearing efficiency, and the two swing arms are symmetrically arranged and move in opposite directions, which can cancel each other out of inertial force to a certain extent and reduce the vibration of the whole machine.

[0032] Furthermore, two eccentric shafts are symmetrically positioned at both ends of the motor's axial direction, with the output shaft as the axis of symmetry.

[0033] By adopting the above technical solution, the two eccentric shafts are symmetrically set with the output shaft as the axis of symmetry, so that the transmission angle and force state of the two transmission plates are consistent, ensuring the symmetry and synchronization of the movement of the two swing arms, and further reducing the vibration caused by asymmetry.

[0034] Furthermore, a transmission arm extends from the lower end of the swing arm, and a pin is provided at the end of the transmission arm. One end of the transmission plate is rotatably connected to the eccentric shaft through a bearing, and the other end of the transmission plate is rotatably connected to the pin through another bearing.

[0035] By adopting the above technical solution, the connection point between the transmission plate and the swing arm is moved from the swing arm body to a position close to the height of the eccentric shaft, so that the bearings at both ends of the transmission plate are closer in the Z-axis direction, the transmission plate is more stable in the transmission process, and the additional vibration caused by the tilt of the transmission plate is reduced.

[0036] Furthermore, the transmission arm extends downward from the swing arm so that the axes of the two bearings are positioned close together in the Z-axis direction.

[0037] By adopting the above technical solution, the transmission arm extends downward from the swing arm, making the bearings at both ends of the transmission plate close in the Z-axis direction. The transmission plate remains in a nearly horizontal state during operation, resulting in higher transmission efficiency and less vibration.

[0038] Furthermore, the connection point between the transmission arm and the swing arm is located in the middle of the swing arm.

[0039] By adopting the above technical solution, the connection position between the transmission arm and the swing arm is located in the middle of the swing arm, so that the driving force of the transmission plate acts on the central area of ​​the swing arm, the swing arm is subjected to balanced force, and the swing arm deflection or swaying caused by the offset drive is avoided, thus improving the stability of the movement.

[0040] Furthermore, an elastic buffer is provided between the two swing arms.

[0041] By adopting the above technical solution, an elastic buffer is provided between the two swing arms. When the swing arm moves to the limit position, it absorbs the impact energy, reduces the vibration and noise when the swing arm reverses direction, and at the same time, the elastic force of the elastic buffer can assist the swing arm to reset, reducing the motor load.

[0042] Furthermore, on adjacent sides of the two swing arms, one is provided with a first mounting seat and the other with a second mounting seat, and the elastic buffer is installed between the first mounting seat and the second mounting seat respectively.

[0043] By adopting the above technical solution, a first mounting seat and a second mounting seat are respectively provided on the adjacent sides of the two swing arms, and the elastic buffer is installed between the first mounting seat and the second mounting seat. The mounting seat provides a special mounting and positioning structure for the elastic buffer, ensuring that the force direction of the elastic buffer is consistent with the movement direction of the swing arm, thus achieving the best buffering effect.

[0044] Furthermore, the second mounting base is located at both ends of the side of any one of the swing arms, and the first mounting base is located in the middle of the side of the other swing arm.

[0045] By adopting the above technical solution, the second mounting base is located at both ends of the side of the swing arm, and the first mounting base is located in the middle of the side of the other swing arm, forming a three-point support elastic buffer layout. The buffer force is more evenly distributed, and the swing arm is more stable in posture during movement.

[0046] Furthermore, the second mounting base is located at one end of the side of either swing arm, and the first mounting base is located at the end of the side of the other swing arm away from the second mounting base.

[0047] By adopting the above technical solution, the second mounting base is located at one end of the side of the swing arm, and the first mounting base is located at the end of the other swing arm away from the second mounting base. The elastic buffer is arranged along the length of the swing arm, and its two ends act on the two swing arms respectively. It can provide a buffer force distributed along the length direction when the swing arm moves, and adapt to the buffering needs of different positions.

[0048] Furthermore, the first and second mounting bases are provided with mounting protrusions at the positions where the elastic buffer is mounted, in order to support the elastic buffer.

[0049] By adopting the above technical solution, the first mounting base and the second mounting base are provided with mounting protrusions to support the elastic buffer, prevent the elastic buffer from shifting or falling off during repeated compression and release, and ensure that the elastic buffer is installed reliably.

[0050] Furthermore, the elastic buffer components are composed of damping springs, compression springs, torsion springs, metal springs, rubber, silicone, and plastic spring structures.

[0051] By adopting the above technical solution, the elastic buffer is a standard elastic component such as a damping spring or a compression spring, which is low in cost, has stable elastic characteristics, is easy to select and replace, and allows for flexible selection of appropriate elastic component specifications according to the buffering requirements of different products.

[0052] Furthermore, the linear drive mechanism also includes a counterweight, with counterweight grooves formed on the first mounting base and / or the second mounting base for mounting the counterweight.

[0053] By adopting the above technical solution, a counterweight groove is formed on the first mounting base and / or the second mounting base for installing a counterweight block. When the two sets of transmission mechanisms experience unequal forces due to differences in the weight or friction of the cutter groups, precise compensation can be achieved by installing a counterweight block of appropriate weight in the counterweight groove, thus balancing the forces on the two sets of transmission mechanisms, canceling out inertial forces, and reducing overall machine vibration. This design allows the motor module to be adapted to cutter groups of different weights without modification, improving the module's versatility. Simultaneously, the counterweight adjustment is convenient and facilitates precise adjustment of minute weight differences.

[0054] Furthermore, the swing arm includes a first swing arm and a second swing arm arranged side by side on the outside of the motor along the axial direction of the motor. The first swing arm and the second swing arm are respectively provided with a drive head. The drive head includes a mounting rod for connecting with the swing arm and a mounting head for mounting a moving cutter head. The mounting rod of the drive head on the first swing arm is connected to the second swing arm, and the mounting rod of the drive head on the second swing arm is connected to the first swing arm, so that the two mounting rods are arranged crosswise and there is a gap between them in a first direction.

[0055] By adopting the above technical solution, the drive head on the first swing arm is connected to the second swing arm via a mounting rod, and the drive head on the second swing arm is connected to the first swing arm via a mounting rod. The two mounting rods are arranged crosswise and have a gap in the first direction. Since the plane of the elastic support plate is parallel to the output shaft axis and perpendicular to the first direction, it has high rigidity in the non-moving direction. When the drive head is subjected to vertical pressure, the pressure is transmitted through the crosswise mounting rods, generating a component force with a definite direction pointing into the motor. This avoids the transmission system shaking caused by component forces in other directions due to installation accuracy or other factors, which is beneficial for improving operating noise and extending service life.

[0056] A linear drive mechanism, comprising:

[0057] The swing arm is used to mount the moving cutter head. The swing arm is located on the outside of the motor along the radial direction of the motor.

[0058] The motor has an eccentric shaft mounted on its output shaft, and the eccentric shaft is arranged parallel to the output shaft.

[0059] The transmission plate is located at the axial end of the motor. One end of the plate is rotatably connected to the eccentric shaft, and the other end is rotatably connected to the swing arm, so as to convert the circumferential motion of the eccentric shaft around the output shaft into the reciprocating linear motion of the swing arm along the first direction.

[0060] The housing and motor are respectively installed inside the housing. A linear sliding mechanism is provided between the swing arm and the housing to slide the swing arm on the housing along the first direction.

[0061] By adopting the above technical solution, a linear sliding mechanism is set between the swing arm and the housing to replace the elastic support plate and realize the linear motion guidance of the swing arm. The linear sliding mechanism can be a slide rail, a slider structure, or a guide rod set on the swing arm, while the housing has a guide hole. The guide rod slides in the guide hole, which can also play a linear guiding role for the swing arm. The linear sliding mechanism can also be other guiding methods. The solution is highly flexible and can select a suitable guiding method according to the cost and space requirements of different products. The motor is fixed in the housing, and the housing provides the installation foundation for the entire drive mechanism. The structure is compact and easy to modularly assemble.

[0062] A shaver includes the aforementioned linear drive mechanism and a housing. The housing has a fixed blade head, and a movable blade head is located on the side of the fixed blade head. The movable blade head is connected to a swing arm. A transmission arm extends from the lower end of the swing arm, and a pin is located at the end of the transmission arm. One end of the transmission plate is rotatably connected to an eccentric shaft via a bearing, and the other end of the transmission plate is rotatably connected to the pin via another bearing.

[0063] By adopting the above technical solution, a linear drive mechanism is applied to a shaver. A fixed blade head is mounted on the housing, and a moving blade head is connected to a swing arm. The swing arm drives the moving blade head to reciprocate relative to the fixed blade head to trim hair. The transmission arm transmits the power of the transmission plate to the swing arm. Both ends of the transmission plate are rotatably connected to an eccentric shaft and a pin on the transmission arm via bearings, resulting in smooth transmission, minimal wear, and a long service life.

[0064] The advantages of this invention are as follows: Compared to the prior art scheme that uses an eccentric shaft sliding within the guide groove of the moving tool holder to drive its reciprocating motion, this application achieves a radially and axially misaligned layout by placing the swing arm radially outside the motor and the transmission plate at the axial end of the motor. One end of the transmission plate is rotatably connected to the eccentric shaft, and the other end is rotatably connected to the swing arm. The circumferential motion of the eccentric shaft is transmitted to the swing arm through the transmission plate. Since both ends of the transmission plate are rotatably connected, the sliding friction between the eccentric shaft and the guide groove wall in the prior art is transformed into rotational friction, effectively reducing friction loss and operating noise during transmission.

[0065] Based on this, a sheet-like elastic support plate is connected between the swing arm and the motor. This elastic support plate simultaneously provides a restoring force to the swing arm and constrains its movement direction. The plane of the sheet-like elastic support plate is parallel to the output shaft axis and perpendicular to the first direction, giving it high rigidity in the direction perpendicular to the first direction. This effectively constrains the non-movement displacement of the swing arm, replacing the guide grooves and other guiding structures that need to be independently installed on the moving tool holder in existing technologies. Simultaneously, the elastic support plate can be elastically bent within its plane, providing an elastic restoring force to the swing arm along the first direction, replacing the separate restoring component required in traditional solutions. This multi-functional design significantly simplifies the number of parts and assembly processes, reducing manufacturing costs.

[0066] Furthermore, this invention, by positioning the swing arm radially outside the motor and the transmission plate axially at the motor's end, creates a radially and axially offset arrangement between the swing arm, transmission plate, and motor. This differs from the coaxial arrangement in existing technologies where the connecting rod and swing arm are sequentially arranged along the motor's axial direction. This offset arrangement ensures a smoother motion for the transmission plate as it converts the circular motion of the eccentric shaft into the reciprocating linear motion of the swing arm. Attached Figure Description

[0067] Figure 1 This is a schematic diagram of the linear drive mechanism of the present invention.

[0068] Figure 2 This is an exploded view of the linear drive mechanism structure of the present invention.

[0069] Figure 3 This is a schematic diagram of the structure of the transmission plate of the present invention (first embodiment of the transmission plate).

[0070] Figure 4 This is a schematic diagram of the linear drive mechanism of the present invention.

[0071] Figure 5 This is a schematic diagram of the linear drive mechanism of the present invention.

[0072] Figure 6 This is a schematic diagram of the linear drive mechanism of the present invention.

[0073] Figure 7 This is a front view of the linear drive mechanism structure of the present invention.

[0074] Figure 8 The transmission plate of the present invention is arranged linearly (third embodiment of the transmission plate).

[0075] Figure 9 For the present invention Figure 4 Top view of the linear drive mechanism.

[0076] Figure 10 This is a schematic diagram of the structure of the transmission plate of the present invention (second embodiment of the transmission plate).

[0077] Figure 11 This is a schematic diagram of the structure of the shaver of the present invention.

[0078] In the picture:

[0079] 1. Motor, 11. Stator, 12. Rotor, 13. Output shaft, 14. Eccentric shaft, 15. Motor housing, 151. Motor mount.

[0080] 2. Swing arm, 21. First swing arm, 22. Second swing arm, 23a. First mounting base, 23b. Second mounting base, 23c. Mounting protrusion, 23d. Counterweight groove, 23e. Bolt, 24f. Counterweight block, 24. Transmission arm, 241. Pin.

[0081] 3. Elastic support sheet.

[0082] 4. Transmission plate, 41. Outer rod, 412. First shaft hole, 411. First thinning section, 42. Inner rod, 421. Second thinning section, 422. Second shaft hole, 43. Bearing, 431. Bearing sleeve.

[0083] 5. Elastic buffer components.

[0084] 6 drive head, 61 mounting head, 62 mounting rod.

[0085] 7. Move the cutter head.

[0086] 81. Machine housing; 82. Fixed cutter head. Detailed Implementation

[0087] The present invention will be further described in detail below with reference to the accompanying drawings and embodiments.

[0088] like Figure 1-11 As shown, this embodiment provides a linear drive mechanism commonly used in reciprocating hair trimming products, such as reciprocating shavers and hair clippers. It includes a motor 1, a swing arm 2, a transmission plate 4, and an elastic support plate 3. The motor 1 includes a stator 11, a rotor 12, and a motor housing 15. The stator 11 and rotor 12 are housed within the motor housing 15. An output shaft 13 extends from the end of the motor housing 15, and an eccentric shaft 14 is mounted on the output shaft 13. The eccentric shaft 14 is parallel to the output shaft 13. The transmission plate 4 is located at the axial end of the motor 1. One end of the transmission plate 4 is rotatably connected to the eccentric shaft 14, and the other end is rotatably connected to the swing arm 2. When the motor 1 drives the eccentric shaft 14 to make circular motion around the output shaft 13, the circular motion of the eccentric shaft 14 is converted into the reciprocating linear motion of the swing arm 2 along the first direction through the transmission plate 4. The motor housing 15 is provided with a motor base 151. The upper end of the elastic support plate 3 is connected to the end of the swing arm 2, and its lower end is correspondingly installed on the motor base 151 of the motor 1.

[0089] For ease of description, such as Figure 1 As shown, the axial direction of the output shaft 13 is the X-axis, the first direction is the Y-axis, and the direction that is perpendicular to both the X-axis and the Y-axis is the Z-axis. That is, the x-axis corresponds to the width direction of the mechanism, the Y-axis corresponds to the length direction, and the z-axis corresponds to the height direction.

[0090] In this embodiment, the elastic support plate 3 has high stiffness in the direction perpendicular to the Y-axis, that is, the elastic support plate 3 can only deform elastically in the Y-axis direction, but cannot deform in the x-axis direction and z-axis direction. This can effectively constrain the non-motion direction displacement of the swing arm 2. At the same time, the elastic support plate 3 can be elastically bent in the plane where its plate shape is located, providing the swing arm 2 with an elastic restoring force in the first direction.

[0091] Compared to the existing technology that uses an eccentric shaft 14 sliding within the guide groove of the moving tool holder to drive the reciprocating motion of the moving tool, this embodiment arranges the swing arm 2 radially on the outside of the motor 1 and the transmission plate 4 axially at the end of the motor 1, creating a radially and axially misaligned layout between the swing arm 2, the transmission plate 4, and the motor 1. Both ends of the transmission plate 4 are rotatably connected, transforming the sliding friction between the eccentric shaft 14 and the guide groove wall in the existing technology into rotational friction, effectively reducing friction loss and operating noise during transmission. Simultaneously, the elastic support plate 3 serves multiple purposes, simultaneously providing guidance and resetting functions, replacing the separately installed guide groove and resetting component in the existing technology, significantly simplifying the number of parts and assembly processes, and reducing manufacturing costs.

[0092] As a further improvement to the above basic embodiment, the transmission plate 4 is provided with an elastic deformation region. The elastic deformation region is configured such that the two ends of the transmission plate 4 can generate elastic relative displacement in the X-axis direction and / or the Z-axis direction.

[0093] Specifically, the technical problem solved by elastic deformation in the X-axis direction is as follows: In the actual assembly process of the transmission mechanism, one end of the transmission plate 4 is rotatably connected to the eccentric shaft 14, and the other end is rotatably connected to the swing arm 2. The rotatable connection at both ends involves the assembly and fitting of multiple parts. The eccentric shaft 14 is mounted on the output shaft 13 of the motor 1. The rotor assembly, stator assembly, and output shaft 13 itself inside the motor 1 have manufacturing tolerances. The installation of the swing arm 2 also has dimensional and assembly tolerances. After these tolerances accumulate at multiple levels, the rotatable connection points at both ends of the transmission plate 4 cannot be completely aligned in the X-axis direction. When the transmission plate 4 is a completely rigid structure, this axial deviation will cause additional axial stress at the rotatable connection points at both ends, resulting in poor rotation, jamming, and significant operating noise. This embodiment sets an elastic deformation zone that can generate elastic relative displacement in the X-axis direction, allowing the transmission plate 4 to absorb this axial assembly deviation through its own elastic deformation in the X-axis direction. This allows the rotatable connection points at both ends to rotate normally without axial stress, avoiding jamming and noise caused by assembly tolerances, and ensuring smooth and stable transmission.

[0094] The technical problem solved by the elastic deformation in the Z-axis direction: During the operation of the transmission mechanism, the eccentric shaft 14 rotates around the output shaft 13, driving the swing arm 2 to reciprocate along the first direction via the transmission plate 4. When the swing arm 2 reaches the limit position of the reciprocating stroke, the direction of motion of the eccentric shaft 14 is about to reverse. At this time, the transmission plate 4 needs to apply a reverse pulling force to the swing arm 2 to reverse its direction. Since the swing arm 2 and the moving cutter head 7 mounted on it have a certain inertia, at the moment of reversal, the inertial force will generate an impact load on the rotating connection at both ends of the transmission plate 4, causing vibration and noise. Long-term operation will also accelerate the wear of the rotating connection and shorten its service life. This embodiment sets an elastic deformation zone that can generate elastic relative displacement in the Z-axis direction. When the swing arm 2 moves to the limit position along the Y-axis direction and generates a reversing impact, the elastic deformation zone can absorb the impact energy through its own elastic deformation in the Z-axis direction, playing a buffering and shock-absorbing role, so that the rotating connection at both ends of the transmission plate 4 is protected from rigid impact, reducing vibration and operating noise, and extending the service life of the transmission mechanism.

[0095] Synergistic Effect of X-axis and Z-axis Elastic Deformation: In actual working conditions, axial deviation caused by assembly tolerances and vertical vibration caused by reversing impacts often coexist and exacerbate each other. Axial deviations worsen the stress state at the rotating connection points at both ends, making it easier to generate non-axial yaw torques under reversing impacts, further amplifying vibrations and noise; while the vibrations generated by reversing impacts accelerate local wear caused by assembly deviations, forming a vicious cycle. This embodiment simultaneously sets elastic deformation zones in both the X-axis and Z-axis directions, making the transmission plate 4 a flexible transmission plate with flexible deformation capabilities in both orthogonal directions in space. This can simultaneously resolve the two mutually exacerbating problems of assembly deviations and motion impacts: the elastic deformation in the X-axis direction absorbs axial assembly deviations, keeping the rotating connection points at both ends in a normal working posture and reducing the additional yaw torque caused by posture deviations during reversing; the elastic deformation in the Z-axis direction absorbs reversing impact energy, preventing the impact load from being transmitted to the assembly deviation point through a rigid connection, avoiding stress concentration and accelerated wear at the deviation point. The combined effect of both methods fundamentally breaks the vicious cycle of assembly deviation—impact amplification—wear aggravation, achieving a comprehensive effect of vibration reduction, noise reduction, and service life extension that is greater than the sum of its parts.

[0096] In one specific embodiment, the elastic deformation zone is a thinned section disposed on the transmission plate 4, the thickness of which is less than that of the adjacent portion of the transmission plate 4. The elastic deformation function can be achieved by local thinning, which is simple to process and does not require additional parts or material changes. It achieves flexible deformation capability in a specific direction while ensuring the structural strength of the main body of the transmission plate 4.

[0097] In another alternative implementation, such as Figure 8 As shown, the elastic deformation zone is composed of a material with an elastic modulus lower than that of the adjacent parts of the transmission plate 4, and can be molded by two-color injection molding, insert injection molding, etc. Compared with the structural thinning method, the material difference method can make the overall thickness of the transmission plate 4 consistent, resulting in a more regular appearance. At the same time, the material properties of the elastic deformation zone can be selected independently as needed, providing greater design flexibility.

[0098] like Figure 1 and 10 As shown, in a preferred embodiment, the transmission plate 4 includes an inner rod 42 extending along the Y-axis and an outer rod 41 disposed on the upper and / or lower side of the inner rod 42. One end of the outer rod 41 is bent to connect with one end of the inner rod 42, the other end of the outer rod 41 is rotatably connected to the swing arm 2, and the other end of the inner rod 42 is rotatably connected to the eccentric shaft 14. The elastic deformation zone includes a first thinning section 411 on the outer rod 41 with a reduced thickness along the Z-axis, and a second thinning section 421 on the inner rod 42 with a reduced thickness along the X-axis.

[0099] As a specific first embodiment of transmission plate 4:

[0100] Reference Figure 1 and 3 As shown, outer rods 41 are provided on both the upper and lower sides of the inner rod 42. One end of each outer rod 41 is bent and connected to one end of the inner rod 42. Preferably, the two are integrally formed, and the entire transmission plate 4 forms a heart-shaped or elliptical structure. The other ends of the two outer rods 41 are connected and rotatably connected to the swing arm 2. The end of the inner rod 42 away from the connection point with the outer rods 41 is rotatably connected to the eccentric shaft 14. The outer rods 41 have a longer extension length in the Y-axis direction, which facilitates the arrangement of the first thinning section 411; the inner rod 42 extends along the Y-axis direction, which facilitates the arrangement of the second thinning section 421. The two thinning sections are respectively set on different components, each solving the elastic deformation requirements in different directions. The functions are clearly divided and the structure is compact.

[0101] As another alternative to the transmission plate 4, a second embodiment is as follows:

[0102] like Figure 10 As shown, an outer rod 41 is provided only on the upper side of the inner rod 42, or only on the lower side of the inner rod 42, forming a half-heart-shaped structure. One end of the outer rod 41 is bent and connected to one end of the inner rod 42, and the other end of the outer rod 41 is rotatably connected to the swing arm 2. The other end of the inner rod 42 is rotatably connected to the eccentric shaft 14. Compared with the scheme of setting outer rods 41 on both sides, this structure is simpler and has a lower manufacturing cost. At the same time, a second thinning section 421 can still be set on the inner rod 42, and a first thinning section 411 can be set on the outer rod 41 to meet the requirements of bidirectional elastic deformation.

[0103] In this embodiment, the inner rod 42 has a second shaft hole 422 at the end away from the bend connection of the outer rod 41, which is used to rotatably connect with the eccentric shaft 14 via a bearing 43. The outer rod 41 has a first shaft hole 412 at the end away from the second shaft hole 422, which is used to rotatably connect with the swing arm 2 via a bearing 43.

[0104] As another alternative third embodiment of the transmission plate 4:

[0105] like Figure 8 As shown, in another alternative embodiment, the transmission plate 4 is a linear sheet structure, with its two ends rotatably connected to the eccentric shaft 14 and the swing arm 2, respectively. Its middle portion has a first thinning section 411 with thickness decreasing along the Z-axis and a second thinning section 421 with thickness decreasing along the X-axis. The linear sheet structure is the simplest to process and can be formed in one step by stamping or injection molding, resulting in low manufacturing costs.

[0106] Based on the above embodiments, the transmission plate 4 can also be made of a material with a low elastic modulus. For example, two different materials can be set in the transmission plate 4 along the y-axis direction to provide elastic deformation capability in the X-axis and Z-axis directions using different materials. Possible materials include: POM plastic, nylon plastic, rubber, silicone, injection molded soft rubber, etc.

[0107] As another alternative fourth embodiment of the transmission plate 4: the transmission plate 4 may also be a spring with a high elastic modulus, which is rigid along its axis, i.e., the Y-axis direction, and has a certain elastic deformation in the x-axis and z-axis directions, and can also achieve the above-mentioned effect.

[0108] It is understood that the above embodiments are merely several specific implementations of the transmission plate 4 of the present invention, and are not an exhaustive list or limitation of the scope of protection of the present invention. Any structural form that, under the guidance of the technical concept of the present invention, enables the transmission plate 4 to generate elastic deformation in the X-axis direction and / or Z-axis direction to achieve the function of absorbing assembly deviations and / or buffering reversing impacts, should be considered to fall within the scope of protection of the present invention.

[0109] In the above embodiments, the specific connection method between one end of the transmission plate 4 and the swing arm 2 can be: a pin 241 is provided on the side of the swing arm 2 (see attached figure). Figure 2 The first shaft hole 412 of the transmission plate 4 is provided with a bearing 43, and is rotatably connected to the pin 241 through the bearing 43, thus realizing the rotatable connection between the transmission plate 4 and the swing arm 2. Of course, it can be imagined that the pin 241 can also be provided at one end of the transmission plate 4 where the first shaft hole 412 is provided, and the corresponding first shaft hole 412 can also be provided on the swing arm 2.

[0110] like Figure 1 As shown in Figure 7, in the above embodiments, one end of the transmission plate 4 is directly rotatably mounted on the swing arm 2. To optimize the transmission structure, further reduce transmission vibration and noise, and improve transmission efficiency, in a preferred embodiment, a transmission arm 24 extends from the lower end of the swing arm 2. The end of the transmission arm 24 is provided with a pin 241. One end of the transmission plate 4 is rotatably connected to the eccentric shaft 14 via a bearing 43, and the other end of the transmission plate 4 is rotatably connected to the pin 241 via another bearing 43. Specifically, the bearing 43 is installed in the first shaft hole 412 and the second shaft hole 422 of the transmission plate 4. A bearing sleeve 431 is fitted over the bearing 43 to protect it and improve rotational smoothness. The transmission arm 24 extends downward from the swing arm 2, making the axis a of the bearing in the first shaft hole 412 and the axis b of the bearing in the second shaft hole 422 close in the Z-axis direction. During operation, the transmission plate 4 remains nearly horizontal, resulting in higher transmission efficiency and less vibration.

[0111] In a more preferred embodiment, the connection position between the transmission arm 24 and the swing arm 2 is located in the middle position of the swing arm 2, so that the driving force of the transmission plate 4 acts on the central area of ​​the swing arm 2, the swing arm 2 is subjected to balanced force, and the swing arm 2 is prevented from deflecting or swaying due to the bias drive, thereby improving the stability of the movement.

[0112] Based on the above embodiments, on the one hand, the transmission arm 24 lowers the connection point between the swing arm 2 and the transmission plate 4 to a height close to the eccentric shaft 14, so that the bearing axis a in the first shaft hole 412 and the bearing axis b in the second shaft hole 422 are close in position in the Z-axis direction, and the transmission plate 4 remains nearly horizontal during operation. Based on this structure, the elastic deformation zone in the X-axis direction on the transmission plate 4 can absorb the positional deviation of the two bearing axes in the X-axis direction caused by assembly tolerances, allowing the inner and outer rings of the bearing 43 to rotate normally without axial stress, avoiding bearing wear and noise caused by assembly deviations.

[0113] On the other hand, when the swing arm 2 moves to its limit position and generates a reversing impact, the elastic deformation zone in the Z-axis direction absorbs the impact energy through its own elastic deformation, preventing the impact load from being rigidly transmitted to the balls and inner and outer rings of the bearing 43. This avoids rigid impact between the bearing balls and the inner and outer ring walls, thereby reducing wear on the bearing 43, lowering operating noise, and extending the bearing's service life. The synergistic effect of elastic deformation in both directions fundamentally protects the operating accuracy and lifespan of the bearings 43 at both ends of the transmission plate 4.

[0114] For ease of understanding, it should be noted that the appendix to this embodiment... Figure 1 None of the above figures show the corresponding embodiment when the transmission plate 4 and the swing arm 2 are rotatably connected. The above figures are all figures of the swing arm 2 with the transmission arm 24 provided.

[0115] In this embodiment, two swing arms 2 are provided, including a first swing arm 21 and a second swing arm 22, which are arranged side by side on the outside of the motor 1 along the axial direction of the motor 1. Eccentric shafts 14 and transmission plates 4 are provided at both ends of the axial direction of the motor 1. The eccentric shafts 14 are connected to the corresponding swing arms 2 via the transmission plates 4. The two eccentric shafts 14 are symmetrically arranged at both ends of the axial direction of the motor 1 with the output shaft 13 as the axis of symmetry. The two swing arms 2 can drive two sets of moving cutter heads 7 respectively, realizing synchronous operation of multiple cutter heads and improving shearing efficiency. The two swing arms 2 are symmetrically arranged and move in opposite directions, which can cancel each other out of inertial force to a certain extent and reduce the vibration of the whole machine.

[0116] like Figure 1 , Figure 2 and Figure 9As shown, in a preferred embodiment, an elastic buffer 5 is provided between the two swing arms 2. The elastic buffer 5 is used to absorb impact energy when the swing arm 2 moves to the limit position, reduce the vibration and noise when the swing arm 2 reverses direction, and at the same time, the elastic force of the elastic buffer 5 can assist the swing arm 2 to reset, reducing the load on the motor 1.

[0117] Specifically, on adjacent sides of the two swing arms 2, one is provided with a first mounting seat 23a, and the other with a second mounting seat 23b. The elastic buffer 5 is installed between the first mounting seat 23a and the second mounting seat 23b. The first mounting seat 23a and the second mounting seat 23b have mounting protrusions 23c at the positions where the elastic buffer 5 is installed, to support the elastic buffer 5 and prevent it from shifting or falling off during repeated compression and release. The elastic buffer 5 can be made of standard elastic components such as damping springs, compression springs, torsion springs, metal springs, rubber, silicone, or plastic springs. These components are low in cost, have stable elastic characteristics, and are easy to select and replace. Appropriate elastic component specifications can be flexibly selected according to the buffering requirements of different products. Of course, it is conceivable that the elastic buffer 5 can also be other components that can buffer or absorb vibration energy, which will not be elaborated upon here.

[0118] As a first embodiment of elastic buffer 5:

[0119] like Figure 1 - Figure 9 As shown, the second mounting base 23b is located at both ends of the side of any one of the swing arms 2, and the first mounting base 23a is located at the middle of the side of the other swing arm 2. Referring to Figure 2, taking the middle of the side of the second swing arm 22 as an example, and the two mounting bases 23b at both ends of the side of the first swing arm 21 as an example, there are two elastic buffer members 5. The two elastic buffer members 5 are symmetrically arranged with the first mounting base 23a as the center. The two elastic buffer members 5 are respectively installed between the first mounting base 23a and the two second mounting bases 23b, forming a symmetrical elastic buffer layout with three-point support.

[0120] In this symmetrical layout, when the two swing arms 2 move relative to each other, as follows: Figure 9As shown, the two swing arms 2 are moved away from each other to their extreme positions, one elastic buffer 5 is compressed, and the other elastic buffer 5 is extended. The compressed elastic buffer 5 absorbs the impact force, reduces vibration, and stores elastic potential energy. At the same time, the extended elastic buffer 5 releases elastic potential energy, which is transmitted to the swing arm 2 through the corresponding mounting base, assisting the transmission plate 4 in driving the swing arm 2 to do work, reducing the amount of work done by the motor 1, and achieving a more energy-saving effect. In the natural state, the two elastic buffers 5 are in a stable state with forces on both sides, and the work done by the elastic buffers 5 on the system is close to zero. The swing arm 2 is in the middle position, at which time the deformation size of the two elastic buffers 5 is the same, the entire system is subjected to balanced forces, and the operation is stable. When the elastic buffer 5 is extended, the effect of pushing the swing arm 2 can be synchronously transmitted to the eccentric shaft 14 at the other end, doing work on the transmission plate 4 and the swing arm 2 at the other end. The absorption of impact force when the elastic buffer 5 is compressed can also benefit the parts driven by the eccentric shaft 14 at the other end, absorbing impact force and reducing vibration.

[0121] As a second embodiment of the elastic buffer:

[0122] In another alternative embodiment, the second mounting base 23b is located at one end of the side of any swing arm 2, and the first mounting base 23a is located at the end of the side of the other swing arm 2 away from the second mounting base 23b. The elastic buffer 5 is arranged diagonally along the length of the swing arm 2, and can provide a buffering force distributed along the length direction when the swing arm 2 moves, adapting to the buffering needs of different positions. That is, in this case, the elastic buffer 5 is a whole damping spring.

[0123] Based on the above embodiments, such as Figure 4 As shown, in a preferred embodiment, a counterweight groove 23d is formed on the first mounting base 23a and / or the second mounting base 23b for mounting the counterweight block 24f. The counterweight block 24f can be fixed in the counterweight groove 23d by bolts 23e.

[0124] When the two transmission mechanisms experience unequal forces due to differences in cutter weight or friction, precise compensation can be achieved by installing a counterweight block 24f of appropriate weight in the counterweight groove 23d. This balances the forces on the two transmission mechanisms, cancels out inertial forces, and reduces overall machine vibration. This design allows the motor module to be adapted to cutter groups of different weights without modification, improving the module's versatility. Furthermore, the counterweight adjustment is convenient and facilitates precise adjustment of minute weight differences.

[0125] like Figures 5 to 7As shown, in a preferred embodiment, a drive head 6 is provided on the first swing arm 21 and the second swing arm 22 respectively. The drive head 6 includes a mounting rod 62 for connecting to the swing arm 2 and a mounting head 61 for mounting the moving cutter head 7. The mounting rod 62 of the drive head 6 on the first swing arm 21 is connected to the second swing arm 22, and the mounting rod 62 of the drive head 6 on the second swing arm 22 is connected to the first swing arm 21, so that the two mounting rods 62 are arranged crosswise, and there is a gap between them in a first direction.

[0126] Because the plane of the elastic support plate 3 is parallel to the axial direction of the output shaft 13 and perpendicular to the first direction, it has high rigidity in the non-moving direction. Figure 7 As shown, when the drive head 6 is subjected to a vertical pressure F1, the pressure is transmitted through the cross-shaped mounting rods 62, generating a component force in the direction F2, which is definite and points towards the inside of the motor 1. This avoids the transmission system from shaking due to other component forces caused by installation accuracy or other factors, thus improving operating noise and extending service life. The component force in the direction F2 extends vertically into the motor and tends towards the module centerline. This component force direction is definite, which can prevent other directional forces generated during movement or other directional component forces caused by installation accuracy from deforming or shaking the transmission rod or the entire system in other directions, thus improving noise and lifespan.

[0127] It should be noted that in the above embodiments, the motor 1 can be an internal rotor motor or an external rotor motor, as long as it can drive the eccentric shaft 14 to make circular motion so as to drive the swing arm 2 to reciprocate through the transmission plate 4. It can also be other types of rotary actuators. Again, the type of motor 1 is not specifically limited.

[0128] In this embodiment, the eccentric shaft 14 can be integrally formed with the output shaft 13, or it can be a separate structure. For example, an eccentric wheel structure can be introduced, with the output shaft 13 installed at the center of the eccentric wheel, and the eccentric shaft 14 installed at a position away from the center of the eccentric wheel. That is, the output shaft 13 can be integrally formed with the eccentric shaft 14, or it can be a separate structure. Further details will not be elaborated here.

[0129] like Figure 11 As shown, this embodiment provides a shaver, which includes the linear drive mechanism and housing 81 described in any of the above embodiments. The linear drive mechanism is correspondingly assembled inside the housing 81 of the shaver. The housing 81 is provided with a fixed blade head 82, and a movable blade head 7 is provided on the inner side of the fixed blade head 82. The movable blade head 7 is connected to the swing arm 2 through a drive head 6, so that when the motor 1 drives the swing arm 2 to move, the movable blade head 7 reciprocates linearly on the side of the fixed blade head 82 to achieve hair trimming.

[0130] The following is combined with Figures 1 to 10 The complete working process of the linear drive mechanism of the present invention will be comprehensively described.

[0131] After the motor 1 is powered on, the rotor 12 rotates under the magnetic field of the stator 11, driving the output shaft 13 to rotate. The eccentric shafts 14 at both ends of the output shaft 13 rotate synchronously with the output shaft 13, and the eccentric shafts 14 perform circular motion around the axis of the output shaft 13. The circular motion of the eccentric shafts 14 is transmitted to the swing arm 2 through the transmission plate 4. One end of the transmission plate 4 is rotatably connected to the eccentric shaft 14 through the bearing 43, and the other end is rotatably connected to the pin 241 at the end of the transmission arm 24 through the bearing 43. The transmission arm 24 extends downward from the swing arm 2, transmitting power to the swing arm 2, thereby converting the circular motion of the eccentric shaft 14 into the reciprocating linear motion of the swing arm 2 along the first direction (Y-axis direction). The swing arm 2 drives the drive head 6 mounted on its upper end to reciprocate synchronously. The mounting head 61 on the drive head 6 drives the moving cutter head 7 to reciprocate relative to the fixed cutter head, realizing the shearing function.

[0132] During transmission, the elastic deformation zone on the transmission plate 4 plays a bidirectional vibration reduction and noise reduction role. In the X-axis direction, since the eccentric shaft 14 is mounted on the output shaft 13, the rotor 12, stator 11 and output shaft 13 inside the motor 1 have manufacturing tolerances, and the installation of the swing arm 2 and transmission arm 24 also has dimensional and assembly tolerances. After these tolerances accumulate through multiple levels, the axes of the bearings 43 at both ends of the transmission plate 4 cannot be completely aligned in the X-axis direction. The transmission plate 4 absorbs this axial assembly deviation in the X-axis direction through the elastic deformation of the second thinning section 421 on the inner rod 42, so that the inner and outer rings of the bearings 43 at both ends can rotate normally without axial stress, avoiding bearing wear, jamming and noise caused by assembly tolerances, and ensuring smooth and stable transmission. In the Z-axis direction, when the swing arm 2 reaches the limit position of its reciprocating stroke, the movement direction of the eccentric shaft 14 is about to reverse. The transmission plate 4 needs to apply a reverse pulling force to the swing arm 2 to reverse its direction. The swing arm 2 and the drive head 6 and moving cutter head 7 mounted on it have a certain motion inertia. The impact load generated at the moment of reversal is absorbed by the elastic deformation of the first thinning section 411 on the outer rod 41 in the Z-axis direction, so that the impact load is not rigidly transmitted to the balls and inner and outer rings of the bearing 43, avoiding rigid impact between the bearing balls and the inner and outer ring walls, thereby reducing vibration and operating noise and extending the service life of the bearing 43. The synergistic effect of elastic deformation in the two directions fundamentally blocks the vicious cycle of assembly deviation—impact amplification—wear aggravation, achieving the technical effect of comprehensive vibration reduction, noise reduction and service life extension.

[0133] During the reciprocating motion of the swing arm 2, the elastic support plate 3 provides the swing arm 2 with an elastic restoring force along the first direction, assisting the swing arm 2 in resetting during commutation and reducing the load on the motor 1. Simultaneously, the elastic support plate 3 has a plate-like structure, with its plate-like plane parallel to the axial direction of the output shaft 13 and perpendicular to the first direction. This gives the elastic support plate 3 high rigidity in the direction perpendicular to the first direction, effectively constraining the non-motion displacement of the swing arm 2 and ensuring that the swing arm 2 always reciprocates stably along the first direction, replacing the need for independently installed guide grooves and restoring components in traditional solutions.

[0134] When the double swing arm scheme is adopted, the first swing arm 21 and the second swing arm 22 are arranged side by side along the axial direction of the motor 1. The two eccentric shafts 14 are symmetrically arranged at both ends of the axial direction of the motor 1 with the output shaft 13 as the axis of symmetry. The first swing arm 21 and the second swing arm 22 are driven to perform synchronous reciprocating motion in opposite directions through the transmission plate 4 respectively. The inertial forces of the two sets of swing arms cancel each other out to a certain extent, reducing the vibration of the whole machine.

[0135] like Figure 4 As shown, during the relative movement of the two swing arms 2, the elastic buffer 5 located between them plays a role in buffering and energy recovery. Taking a symmetrical layout as an example, the two elastic buffers 5 are symmetrically arranged with the first mounting base 23a as the center. When the two swing arms 2 move away from each other to their extreme positions, one elastic buffer 5 is compressed, absorbing the impact force, reducing vibration, and storing elastic potential energy; at the same time, the other elastic buffer 5 expands, releasing the stored elastic potential energy. This elastic potential energy is transmitted to the swing arm 2 through the mounting base, assisting the transmission plate 4 in driving the swing arm 2 to do work, reducing the amount of work done by the motor 1, and achieving a more energy-saving effect. The impact force absorbed by the compressed elastic buffer 5 can also benefit the parts driven by the eccentric shaft 14 at the other end, reducing vibration. In the natural state, the two elastic buffers 5 are in a stable state with forces on both sides, and the work done on the system is close to zero. The swing arm 2 is in the middle position, at which time the deformation size of the two elastic buffers 5 is the same, the entire system is subjected to balanced forces, and the operation is stable.

[0136] When the two sets of transmission mechanisms experience unequal forces due to differences in the weight or friction of the cutter sets, precise compensation can be achieved by installing a counterweight block 24f of appropriate weight in the counterweight groove 23d on the first mounting base 23a and / or the second mounting base 23b. This balances the forces on the two sets of transmission mechanisms, makes the inertial forces cancel each other out more thoroughly, and further reduces the vibration of the entire machine.

[0137] When the drive head 6 is subjected to vertical pressure, the mounting rod 62 of the drive head 6 on the first swing arm 21 is connected to the second swing arm 22, and the mounting rod 62 of the drive head 6 on the second swing arm 22 is connected to the first swing arm 21. The two mounting rods 62 are arranged in a cross configuration, and the elastic support plate 3 has high rigidity in the non-movement direction. The pressure is transmitted through the cross-arranged mounting rods 62, generating a component force in the direction of F2 that is definite and points into the motor 1. This avoids the transmission system from shaking due to component forces in other directions caused by installation accuracy or other factors, which is beneficial for improving operating noise and extending service life.

[0138] When counterweight adjustment is required, counterweight block 24f can be installed or replaced in counterweight groove 23d and fixed by bolt 23e to balance the force of the two transmission mechanisms; when the moving cutter head 7 needs to be replaced, it can be removed from the mounting head 61 for replacement; when the bearing 43 needs to be maintained, the bearing 43 and bearing sleeve 431 can be removed from the first shaft hole 412 or the second shaft hole 422 of the transmission plate 4 for replacement. The entire mechanism is compact and easy to assemble and maintain.

[0139] It should be noted that the meaning of "razor" in this application is not limited to products used for shaving, but also includes hair clippers or other hair trimming devices.

[0140] Although preferred embodiments of the present invention have been described in detail above, it should be clearly understood that various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A linear drive mechanism, comprising: A swing arm is used to mount the moving cutter head, and the swing arm is arranged radially on the outside of the motor. An electric motor, wherein an eccentric shaft is mounted on its output shaft, and the eccentric shaft is arranged parallel to the output shaft; A transmission plate is provided at the axial end of the motor. One end of the plate is rotatably connected to the eccentric shaft, and the other end is rotatably connected to the swing arm, so as to convert the circumferential motion of the eccentric shaft around the output shaft into the reciprocating linear motion of the swing arm along the first direction. An elastic support plate is installed between the swing arm and the motor to provide the swing arm with an elastic restoring force along a first direction; the elastic support plate is a sheet-like structure, and the plane in which the sheet is located is parallel to the axial direction of the output shaft and perpendicular to the first direction.

2. The linear drive mechanism according to claim 1, characterized in that, The axial direction of the output shaft is taken as the x-axis direction, the first direction is taken as the Y-axis direction, and the direction that is perpendicular to both the x-axis direction and the Y-axis direction is taken as the Z-axis direction. The transmission plate is provided with an elastic deformation zone, which is configured such that the two ends of the transmission plate can generate elastic relative displacement in the x-axis direction and / or the Z-axis direction.

3. A linear drive mechanism according to claim 2, characterized in that, The elastic deformation zone includes a thickness reduction section disposed on the transmission plate, through which the transmission plate generates elastic displacement in the x-axis direction and / or Z-axis direction.

4. A linear drive mechanism according to claim 2, characterized in that, The elastic modulus of the elastic deformation zone is lower than that of other parts of the transmission plate.

5. A linear drive mechanism according to claim 2, characterized in that, The transmission plate includes an inner rod extending along the Y-axis and an outer rod disposed on the upper and / or lower side of the inner rod. One end of the outer rod is bent to connect with one end of the inner rod, and the other end of the outer rod is rotatably connected to the swing arm. The other end of the inner rod is rotatably connected to the eccentric shaft. The elastic deformation zone includes a first thinning section on the outer rod with reduced thickness along the Z-axis direction, and a second thinning section on the inner rod with reduced thickness along the x-axis direction.

6. A linear drive mechanism according to claim 2, characterized in that, The transmission plate is a linear plate structure, with its two ends rotatably connected to the eccentric shaft and the swing arm, respectively. Its middle part is provided with a first thinning section with a thickness reduction along the Z-axis and a second thinning section with a thickness reduction along the x-axis.

7. A linear drive mechanism according to claim 1, characterized in that, Two swing arms are provided, which are arranged side by side on the outside of the motor along the axial direction of the motor. The eccentric shaft and the transmission plate are provided at both ends of the axial direction of the motor. The eccentric shaft is connected to the corresponding swing arm through the transmission plate.

8. A linear drive mechanism according to claim 7, characterized in that, The two eccentric shafts are symmetrically arranged at both ends of the motor axial direction with the output shaft as the axis of symmetry.

9. A linear drive mechanism according to any one of claims 1-8, characterized in that, The lower end of the swing arm extends into a transmission arm, and the end of the transmission arm is provided with a pin. One end of the transmission plate is rotatably connected to the eccentric shaft through a bearing, and the other end of the transmission plate is rotatably connected to the pin through another bearing.

10. A linear drive mechanism according to claim 9, characterized in that, The transmission arm extends downward from the swing arm so that the axes of the two bearings are positioned close together in the Z-axis direction.

11. A linear drive mechanism according to claim 9, characterized in that, The connection point between the transmission arm and the swing arm is located at the middle position of the swing arm.

12. A linear drive mechanism according to claim 7, characterized in that, An elastic buffer is provided between the two swing arms.

13. A linear drive mechanism according to claim 12, characterized in that, On adjacent sides of the two swing arms, one is provided with a first mounting seat and the other with a second mounting seat, and the elastic buffer is installed between the first mounting seat and the second mounting seat respectively.

14. A linear drive mechanism according to claim 13, characterized in that, The second mounting base is disposed at both ends of the side of any of the swing arms, and the first mounting base is disposed at the middle of the side of the other swing arm.

15. A linear drive mechanism according to claim 13, characterized in that, The second mounting base is disposed at one end of the side of either of the swing arms, and the first mounting base is disposed at the end of the side of the other swing arm away from the second mounting base.

16. A linear drive mechanism according to claim 13, characterized in that, The first mounting base and the second mounting base are provided with mounting protrusions at the positions where the elastic buffer is installed, so as to support the elastic buffer.

17. A linear drive mechanism according to claim 12, characterized in that, The elastic buffer is composed of damping springs, compression springs, torsion springs, metal springs, rubber, silicone, or plastic springs.

18. A linear drive mechanism according to claim 13, characterized in that, The linear drive mechanism further includes a counterweight, and a counterweight groove is formed on the first mounting base and / or the second mounting base for mounting the counterweight.

19. A linear drive mechanism according to claim 1, characterized in that, The swing arm includes a first swing arm and a second swing arm arranged side by side on the outer side of the motor along the axial direction of the motor. The first swing arm and the second swing arm are respectively provided with a drive head. The drive head includes a mounting rod for connecting to the swing arm and a mounting head for mounting a moving cutter head. The mounting rod of the drive head on the first swing arm is connected to the second swing arm, and the mounting rod of the drive head on the second swing arm is connected to the first swing arm, so that the two mounting rods are arranged crosswise and there is a gap between them in the first direction.

20. A linear drive mechanism, characterized in that, include: A swing arm is used to mount the moving cutter head, and the swing arm is arranged radially on the outside of the motor. An electric motor, wherein an eccentric shaft is mounted on its output shaft, and the eccentric shaft is arranged parallel to the output shaft; A transmission plate is provided at the axial end of the motor. One end of the plate is rotatably connected to the eccentric shaft, and the other end is rotatably connected to the swing arm, so as to convert the circumferential motion of the eccentric shaft around the output shaft into the reciprocating linear motion of the swing arm along the first direction. The housing contains the motor, and a linear sliding mechanism is provided between the swing arm and the housing to slide the swing arm on the housing along a first direction.

21. A razor, characterized in that, It includes a linear drive mechanism and a housing according to any one of claims 1-8 and 12-20, wherein a fixed cutter head is provided on the housing, a movable cutter head is provided on the side of the fixed cutter head, the movable cutter head is connected to the swing arm, a transmission arm extends from the lower end of the swing arm, a pin is provided at the end of the transmission arm, one end of the transmission plate is rotatably connected to the eccentric shaft through a bearing, and the other end of the transmission plate is rotatably connected to the pin through another bearing.

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