Single gang hinge type miter saw

Abstract

This invention discloses a single-hinged miter saw, belonging to the field of miter saws, which solves the problem of inconsistent horizontal movement height of the saw blade in existing technologies. The technical solution to this problem includes a first hinged arm hinged to the saw head and a second hinged arm hinged to the first hinged arm. A posture-maintaining link is also hinged between the second hinged arm and the saw head. The first hinged arm, the posture-maintaining link, a first link segment between the second hinge point of the first hinged arm and the second hinged arm and the third hinge point of the posture-maintaining link and the second hinged arm, and a second link segment between the fourth hinge point of the posture-maintaining link and the saw head and the first hinge point of the first hinged arm and the saw head together constitute a quadrilateral linkage mechanism. When the first hinged arm flips relative to the second hinged arm and drives the saw head to move laterally, the quadrilateral linkage mechanism constrains the saw head to rotate in the opposite direction relative to the first hinged arm. This invention ensures that the horizontal movement height of the saw blade remains consistent.

Description

Technical Field

[0001] This invention relates to the field of miter saws, and in particular to a single-hinged miter saw. Background Technology

[0002] Traditional miter saws often use a rear tie rod structure to support the saw blade's sliding motion, resulting in a large space occupation at the rear of the machine and making it impossible to operate against a wall. While existing technologies, such as the articulated miter saws proposed in patents CN118204561A and CN217799343U, eliminate rear space occupation by using articulated arms and gear meshing to drive the machine head and saw blade horizontally, the continuous change in pitch angle of the articulated arms during machine head operation, coupled with the lack of dynamic limiting mechanisms in existing solutions to adapt to this movement trajectory, leads to saw blade tipping or tilting, resulting in inconsistent cutting depth and skewed cut surfaces. Summary of the Invention

[0003] The purpose of this invention is to provide a single-hinged miter saw that solves the problem of inconsistent horizontal movement height of the saw blade in the prior art, so that the horizontal movement height of the saw blade is consistent and its application range is wider.

[0004] To achieve the above objectives, the present invention adopts the following technical solution: a single-hinged miter saw, comprising a worktable and a head, wherein a saw blade is mounted on the head, and the head is connected to the worktable via multiple hinged arms that are hinged to each other. A synchronous transmission element is provided between the hinged arms to maintain a constant height at the first hinge point between the hinged arm and the head. Each hinged arm includes a first hinged arm hinged to the head and a second hinged arm hinged to the first hinged arm. A posture-maintaining link is also hinged between the second hinged arm and the head. The first hinged arm, the posture-maintaining link, a first link segment from the second hinge point between the first and second hinged arms to the third hinge point between the posture-maintaining link and the second hinged arm, and a second link segment from the fourth hinge point between the posture-maintaining link and the head to the first hinge point between the first hinged arm and the head together constitute a quadrilateral linkage mechanism. When the first hinged arm flips relative to the second hinged arm and drives the head to move laterally, the quadrilateral linkage mechanism constrains the head to rotate in the opposite direction relative to the first hinged arm.

[0005] After adopting the above technical solution, the present invention has the following advantages: During the process of the first articulated arm flipping relative to the second articulated arm and driving the machine head to move laterally, the geometric constraint characteristics of the quadrilateral linkage mechanism can be used to drive the machine head to generate reverse rotation compensation relative to the first articulated arm, which is opposite to the flipping direction of the first articulated arm. This counteracts the interference of the pitch angle change of the articulated arm on the attitude of the machine head as much as possible. At the same time, the synchronous transmission components between the articulated arms maintain a constant height between the articulated arm and the machine head hinge point. From the structural level, the rigid constraint and stability of the machine head attitude are achieved, so that the machine head can maintain the predetermined attitude as much as possible throughout the entire lateral movement stroke. This ensures that the saw blade height is consistent as much as possible and avoids saw blade tipping and attitude deviation as much as possible. Moreover, the pure mechanical linkage constraint structure does not require additional drive or control components, and the structure is simple and reliable. While retaining the advantages of the articulated structure of no rear space occupation and reliable wall operation, it improves the cutting accuracy and operational stability.

[0006] Furthermore, the lengths of the first link segment, the attitude holding link, the second link segment, and the first articulated arm are all different.

[0007] By adopting the aforementioned technical solution, non-proportional geometric constraints are achieved through differentiated length parameters. This allows the saw head to obtain more precise reverse rotation compensation that matches the pitch changes of the articulated arms throughout the entire rotation of the first articulated arm relative to the second articulated arm. This further ensures that the saw head posture is as stable and free from deviation as possible, and prevents the saw blade from tilting or wobbling. At the same time, it can optimize the motion envelope space of the linkages, reduce the risk of motion interference between the linkages and articulated arms, improve the smoothness of the mechanism's operation and the compactness of the structure, and make the saw blade height more stable throughout the entire sliding stroke of the saw head.

[0008] Furthermore, the length of the attitude-maintaining link is greater than the length of the first hinge arm, and the length of the first link segment is less than the length of the second link segment.

[0009] By adopting the aforementioned technical solution, the motion amplification and compensation ratio of the quadrilateral linkage mechanism is directly changed: the attitude-maintaining linkage is longer than the first articulated arm, which can provide a larger reverse attitude correction stroke for the machine head when the first articulated arm tilts and flips slightly, thus offsetting the saw blade tilting tendency caused by the first articulated arm tilting up or down; the first link segment is shorter than the second link segment, which can reduce the coupling deflection amplitude of the machine head swinging with the first articulated arm, so that the rotational angular velocity of the machine head is less than the flipping angular velocity of the first articulated arm, thus avoiding excessive compensation that could cause the machine head to tilt down or the cutting face to tilt forward. The two work together to ensure that the machine head maintains a horizontal attitude as much as possible throughout the entire lateral movement process, and the saw blade height does not fluctuate up or down.

[0010] Furthermore, the length ratio of the first link segment, the attitude holding link, the second link segment, and the first articulated arm is 10:(105~110):(20~24):(100~104).

[0011] By adopting the aforementioned technical solution, the length of the attitude-maintaining link is greater than that of the first articulated arm, and the first link segment is much shorter than that of the second link segment. When the first articulated arm pitches and swings, the quadrilateral linkage mechanism will generate a small-angle reverse compensation rotation that more precisely matches the range of motion of the first articulated arm. This will prevent the saw blade from tilting due to insufficient compensation angle, and will also prevent the machine head from tilting due to excessive compensation angle. This will keep the machine head as horizontal as possible throughout the entire lateral movement stroke, thereby keeping the saw blade height as constant as possible without fluctuation.

[0012] Furthermore, a limiting plate is also fitted at the hinge shaft between the machine head and the first hinge arm. A limiting groove is formed on the limiting plate, and a limiting pin is fixed on the machine head. The limiting pin extends into the limiting groove. When the limiting plate rotates, the groove wall of the limiting groove pushes against the end wall of the limiting pin to drive the machine head to rotate.

[0013] By utilizing the aforementioned technical solution, the limiting groove on the limiting plate cooperates with the limiting pin fixed on the machine head. When the first articulated arm rotates and drives the machine head to move, the mechanical pushing action of the limiting groove on the limiting pin provides forced posture constraint for the machine head, directly limiting the machine head from unexpected rotation under the influence of its own gravity and cutting recoil force.

[0014] Furthermore, the attitude holding link is hinged to the limiting plate to achieve hinged connection on the machine head.

[0015] Through the above technical solution, the swing of the attitude-keeping linkage can directly drive the limit plate to rotate synchronously, so that the forced constraint angle between the limit groove and the limit pin can be dynamically adjusted in real time with the movement of the linkage. This ensures that the machine head always rotates in a controlled and compensated manner within the limited range of the limit groove, minimizing the free movement and swaying of the machine head. At the same time, the attitude-keeping torque of the attitude-keeping linkage is rigidly transmitted to the machine head through the limit plate, minimizing the attitude deviation caused by force eccentricity when the attitude-keeping linkage is directly hinged to the machine head. After the superposition of the double constraints, the attitude of the machine head is more stable during the cutting reaction force and the swing of the hinged arm, minimizing the occurrence of tilting and deflection, and the consistency between the saw blade height and the cutting angle is higher.

[0016] Furthermore, the limiting groove has a first end and a second end that are disposed opposite to each other along its extending direction, and the machine head has a first position away from the worktable and a second position close to the worktable. When the machine head is moved to the first position by an external force, the limiting pin abuts against the first end to keep the machine head in the first position. When the machine head is moved to the second position by an external force, the limiting pin abuts against the second end to keep the machine head in the second position.

[0017] Through the above technical solution, when the machine head is switched between lifting and pressing down, the limit pin will be pushed by the groove wall and finally abut against the corresponding end position, so as to more accurately realize the reliable switching between the two working positions of lifting the machine head and pressing down cutting. After the machine head reaches the target position, it can achieve rigid limit through hard contact, preventing the machine head from being accidentally lifted, sunk or shaken under the action of cutting vibration, its own weight or external force, and ensuring that the machine head can be more stably maintained in the set posture in both the lifting standby state and the pressing down cutting state.

[0018] Furthermore, an elastic element is provided between the first articulated arm and the machine head, with both ends of the elastic element acting on the first articulated arm and the machine head respectively, to apply an elastic restoring force to the machine head to make it tend toward the first position.

[0019] With the above technical solution, when the machine head is pressed down to the second position for cutting, the elastic element stores elastic potential energy. After the cutting is completed and the external force is removed, the machine head is automatically driven to return to the first position by the elastic restoring force, realizing the automatic switching between pressing down and resetting the machine head. There is no need for manual lifting of the machine, making the operation more labor-saving and efficient.

[0020] Furthermore, the plurality of the hinged arms are arranged in a unidirectional extension and hinged sequentially.

[0021] The above technical solution can form a transmission chain that extends in one direction, avoiding motion interference and spatial redundancy caused by bidirectional or multidirectional hinges as much as possible. When driving the machine head to move laterally, each hinge arm swings in the same direction in coordination only along the same plane, making the motion trajectory clearer and more unified, minimizing mutual interference between components, ensuring smooth and stable transmission, and simplifying the overall layout by arranging the structure in one direction sequentially, making the whole machine structure more compact.

[0022] Furthermore, the synchronous transmission component includes a pin disposed between adjacent hinged arms, a transmission shaft disposed between adjacent pins, and bevel gears disposed on the pins and the transmission shaft, wherein the bevel gears on the pins and the transmission shaft mesh with each other.

[0023] The above technical solution achieves linkage between the articulated arms through bevel gear meshing. By changing the gear ratio between the pin and the bevel gear on the drive shaft, the rotation angle of multiple articulated arms is controlled synchronously. This ensures that the articulated arm and the machine head maintain a constant articulation point height when the articulated arm is unfolded and folded, thereby driving the machine head to achieve smooth horizontal movement at the same height. Attached Figure Description

[0024] The present invention will be further described below with reference to the accompanying drawings:

[0025] Figure 1 This is a schematic diagram of the structure of the single-joint hinged miter saw of the present invention;

[0026] Figure 2 This is a structural schematic diagram of the single-joint hinged miter saw of the present invention from another perspective;

[0027] Figure 3 This is a partial structural schematic diagram of the single-joint hinged miter saw of the present invention;

[0028] Figure 4 This is a partial structural diagram of the single-joint hinged miter saw of the present invention;

[0029] Figure 5 This is a structural schematic diagram of the single-joint hinged miter saw of the present invention from another perspective.

[0030] Figure 6 This is a schematic diagram of the single-joint hinged miter saw of the present invention with the machine head in the first position;

[0031] Figure 7 This is a schematic diagram of the structure of the single-joint hinged miter saw of the present invention, in which the machine head is in the second position;

[0032] Figure 8 This is a schematic diagram of the structure of the single-joint hinged miter saw after the machine head is pulled.

[0033] Figure 9 This is a schematic diagram of the head repositioning structure in the single-joint hinged miter saw of the present invention;

[0034] In the diagram, 10 is the workbench; 11 is the fixed part; 12 is the base part; 13 is the turntable; 131 is the guide groove; 20 is the machine head; 21 is the saw blade; 22 is the motor; 23 is the limit pin; 24 is the handle; 30 is the synchronous transmission component; 301 is the pin shaft; 302 is the transmission shaft; 303 is the bevel gear; 304 is the elastic pin; 31 is the first hinge arm; 32 is the second hinge arm; 33 is the first connecting rod segment; 34 is the second connecting rod segment; 35 is the first hinge point; 36 is the second hinge point; 37 is the third hinge point; 38 is the fourth hinge point; 40 is the posture holding link; 41 is the limit plate; 42 is the limit groove; 43 is the first end; 44 is the second end; and 50 is the elastic component. Detailed Implementation

[0035] 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 embodiments of the present invention, and not all embodiments.

[0036] The terms "first," "second," "third," "fourth," etc. (if present) in the specification, claims, and accompanying drawings of this invention are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that such data can be interchanged where appropriate so that embodiments of the invention described herein can be implemented in orders other than those illustrated or described herein.

[0037] It should be understood that in the various embodiments of the present invention, the number of each process does not imply the order of execution. The execution order of each process should be determined by its function and internal logic, and should not constitute any limitation on the implementation process of the embodiments of the present invention.

[0038] It should be understood that in this invention, "comprising" and "having," and any variations thereof, are intended to cover non-exclusive inclusion, for example, a process, method, system, product, or device that includes a series of steps or units is not necessarily limited to those steps or units explicitly listed, but may include other steps or units not explicitly listed or inherent to such process, method, product, or device.

[0039] It should be understood that in this invention, "multiple" refers to two or more. "And / or" is merely a description of the relationship between related objects, indicating that three relationships can exist. For example, X and / or Y can represent: X alone, X and Y simultaneously, or Y alone. The character " / " generally indicates that the preceding and following related objects are in an "or" relationship. "Contains X, Y, and Z", "Contains X, Y, and Z" means that all three X, Y, and Z are contained; "Contains X, Y, or Z" means that one of X, Y, and Z is contained; "Contains X, Y, and / or Z" means that any one, two, or three of X, Y, and Z are contained.

[0040] The technical solution of the present invention will be described in detail below with reference to specific embodiments. The following specific embodiments may be combined or substituted with each other according to the actual situation, and the same or similar concepts or processes may not be described again in some embodiments.

[0041] like Figures 1 to 9As shown, the present invention provides a single-set hinged miter saw, including a worktable 10 and a saw head 20. The saw head 20 is equipped with a saw blade 21 and a motor 22. The motor 22 drives the saw blade 21 to rotate. The saw head 20 is connected to the worktable 10 via multiple hinged arms that are hinged to each other. A synchronous transmission member 30 is provided between the hinged arms to maintain a constant height between the hinged arms and the first hinge point 35 of the saw head 20. Each hinged arm includes a first hinged arm 31 hinged to the saw head 20 and a second hinged arm 32 hinged to the first hinged arm 31. A posture-maintaining link 40 is also hinged between the second hinged arm 32 and the saw head 20. Arm 31, attitude holding link 40, the first link segment 33 between the second hinge point 36 of the first hinge arm 31 and the second hinge arm 32 and the third hinge point 37 of the attitude holding link 40 and the second hinge arm 32, and the second link segment 34 between the fourth hinge point 38 of the attitude holding link 40 and the head 20 and the first hinge point 35 of the first hinge arm 31 and the head 20 together constitute a quadrilateral linkage mechanism. When the first hinge arm 31 flips relative to the second hinge arm 32 and drives the head 20 to move laterally, the quadrilateral linkage mechanism constrains the head 20 to rotate in the opposite direction relative to the first hinge arm 31.

[0042] During the process of the first articulated arm 31 flipping relative to the second articulated arm 32 to drive the machine head 20 to move laterally, the geometric constraint characteristics of the quadrilateral linkage mechanism can be used to drive the machine head 20 to rotate in the opposite direction relative to the first articulated arm 31 to compensate for the rotation. This directly cancels out the interference of the pitch angle change of the first articulated arm 31 on the attitude of the machine head 20. At the same time, the synchronous transmission component 30 between the articulated arms maintains the height of the first articulated arm 31 and the first articulation point 35 of the machine head 20 at a constant height. This achieves rigid constraint and stable maintenance of the attitude of the machine head 20 from a structural level, so that the machine head 20 maintains the predetermined attitude as much as possible throughout the entire lateral movement stroke. This ensures that the height of the saw blade 21 is consistent as much as possible, and avoids the saw blade 21 tilting or tilting as much as possible. Moreover, the pure mechanical linkage constraint structure does not require additional drive or control components, and the structure is simple and reliable. While retaining the advantages of the articulated structure of no rear space occupation and reliable wall operation, it improves the cutting accuracy and operational stability.

[0043] It should be noted that, for ease of understanding, the lever arms between the quadrilateral linkages are shown with dashed lines. The worktable 10 includes a fixed part 11 and a base part 12. The fixed part 11 is hinged to the second hinge arm 32, and the base part 12 is used to support the worktable on the ground. A turntable 13 is mounted on the base part 12, and the fixed part 11 is located on the turntable 13. The turntable 13 is rotatably mounted on the base part 12. Manually rotating the turntable 13 can change the position of the saw blade 21 relative to the base part 12. The turntable 13 is provided with a guide groove 131, which is a long, narrow through groove. Its extension direction is parallel to the horizontal movement trajectory of the saw head 20, and the guide groove 131 is located below the saw blade 21. The height of the first hinge point 35 between the articulated arm and the machine head 20 is constant, that is, the height of the first hinge point 35 between the first articulated arm 31 and the machine head 20 is constant. At this time, the distance between the first hinge point 35 and the turntable 13 remains unchanged. The machine head 20 is equipped with a handle 24 for easy operation. The handle 24 is arranged away from the saw blade 21 to avoid accidental contact with the saw blade 21 during operation. The operator can push the machine head 20 to move in a straight line by gripping the handle 24.

[0044] Multiple articulated arms are arranged sequentially in one direction and hinged to each other in pairs, assembling to form a unidirectionally extendable transmission chain, constituting an integrated single-set hinge structure. This single-set hinge structure minimizes motion interference problems that easily occur in bidirectional or multidirectional hinge structures, while also reducing redundant space occupation. This effectively avoids motion interference and space waste caused by bidirectional or multidirectional hinges. When the drive head 20 moves laterally, each articulated arm swings in the same direction within the same plane, resulting in a clearer and more consistent motion trajectory, greatly reducing mutual influence between components and ensuring smooth and stable transmission. Moreover, the unidirectional sequential arrangement simplifies the overall structural layout, further compressing the space occupied by the entire machine and making the overall structure more compact. It should be noted that a single-set hinge structure refers to a linear hinge configuration where the ends are not connected.

[0045] The first connecting rod segment 33, the attitude-maintaining connecting rod 40, the second connecting rod segment 34, and the first hinged arm 31 each have different lengths, collectively forming a crank-rocker mechanism. By using different length parameters to achieve non-proportional geometric constraints, the machine head 20 can obtain a more precise counter-rotation compensation matching the pitch change of the hinged arm during the entire process of the first hinged arm 31 flipping relative to the second hinged arm 32. This further ensures that the machine head 20 maintains a stable and unbiased attitude, minimizing the possibility of the saw blade 21 tilting or wobbling. Simultaneously, it optimizes the envelope space of the linkage motion, reducing the possibility of motion interference between the linkage and each hinged arm, thereby improving the smoothness of the mechanism's operation and its structural compactness, making the saw blade 21 height more stable during the sliding stroke of the machine head 20.

[0046] If the length of the attitude-maintaining linkage 40 is greater than the length of the first articulated arm 31, it can provide a larger reverse attitude correction stroke for the saw head 20 when the first articulated arm 31 tilts slightly, thereby counteracting the tendency of the saw blade 21 to tilt upwards or downwards caused by the first articulated arm 31. In addition, the length of the first link segment 33 is less than the length of the second link segment 34, which can reduce the coupling deflection amplitude of the saw head 20 when it swings with the first articulated arm 31, so that the rotational angular velocity of the saw head 20 is lower than the tilting angular velocity of the first articulated arm 31, and prevent the saw head 20 from tilting downwards or tilting forward due to overcompensation as much as possible. The two work together to keep the saw head 20 as horizontal as possible throughout the entire lateral movement, and the height of the saw blade 21 does not fluctuate up and down.

[0047] Constrained by the proportional relationship of the link lengths in the quadrilateral linkage mechanism, the saw head 20 rotates in the opposite direction relative to the first hinge arm 31. This geometric ratio determines the matching state of the rotational speeds between the two, resulting in three variations in the height of the saw blade 21: When the proportional relationship of the link lengths in the quadrilateral linkage mechanism causes the reverse rotational speed of the saw head 20 to be slightly greater than the rotational speed of the first hinge arm 31 relative to the second hinge arm 32, the height of the saw blade 21 will decrease slightly, but this is negligible compared to the original tilting amplitude; When the proportional relationship of the link lengths in the quadrilateral linkage mechanism causes the reverse rotational speed of the saw head 20 to be slightly less than the rotational speed of the first hinge arm 31, the height of the saw blade 21 will increase slightly, but this is negligible compared to the original tilting amplitude; And when the proportional relationship of the link lengths in the quadrilateral linkage mechanism makes the rotational speeds of the two basically equal, the height of the saw blade 21 remains constant. To keep the height of the saw blade 21 as constant as possible, the length ratio of the first link segment 33, the attitude holding link 40, the second link segment 34, and the first articulated arm 31 is 10:(105~110):(20~24):(100~104). This makes the length of the attitude holding link 40 exceed that of the first articulated arm 31, and the first link segment 33 is significantly shorter than the second link segment 34. When the first articulated arm 31 pitches, the quadrilateral linkage mechanism generates a small-angle counter-compensation rotation that more precisely matches the range of motion of the first articulated arm 31. This avoids the saw blade 21 tilting due to insufficient compensation angle as much as possible, and also prevents the head 20 from tilting down due to excessive compensation angle. Thus, the head 20 is kept as horizontal as possible throughout its entire lateral movement, thereby keeping the height of the saw blade 21 as constant as possible without fluctuation.

[0048] Preferably, the length ratio of the first link segment 33, the attitude holding link 40, the second link segment 34, and the first hinge arm 31 is 10:107:22:100, so as to meet the motion compensation requirements of the quadrilateral linkage mechanism. The attitude holding link 40 pulls the limiting plate 41, causing the saw head 20 to rotate relative to the first hinge arm 31, which cancels the angle at which the saw head 20 is raised as it follows the rotation of the first hinge arm 31, so that the attitude of the saw head 20 remains unchanged, so that the saw blade 21 can maintain a consistent height as much as possible.

[0049] A limiting plate 41 is also fitted onto the hinge shaft of the machine head 20 and the first hinge arm 31. The limiting plate 41 is provided with a limiting groove 42, and a limiting pin 23 is fixed on the machine head 20. The limiting pin 23 is inserted into the limiting groove 42. When the limiting plate 41 rotates, the end wall of the limiting groove 42 will push against the surface of the limiting pin 23, thereby driving the machine head 20 to rotate. This provides forced posture constraint for the machine head 20 and directly restricts the machine head 20 from rotating unexpectedly under its own weight and cutting recoil force.

[0050] Preferably, the attitude-maintaining link 40 is hinged to the limiting plate 41 to achieve hinged connection on the machine head 20. The swing of the attitude-maintaining link 40 can directly drive the limiting plate 41 to rotate synchronously, so that the forced constraint angle of the limiting groove 42 and the limiting pin 23 is dynamically adjusted in real time with the movement of the attitude-maintaining link 40, so that the side of the limiting plate 41 always remains at a constant angle with the horizontal line. This ensures that the machine head 20 always rotates within the limited range of the limiting groove 42, avoiding the machine head 20 from moving freely or swaying as much as possible. At the same time, the attitude-maintaining torque of the attitude-maintaining link 40 is rigidly transmitted to the machine head 20 through the limiting plate 41, avoiding attitude deviation caused by force eccentricity when the attitude-maintaining link 40 is directly hinged to the machine head 20. After the superposition of the double constraints, the attitude of the machine head 20 is more stable during the cutting reaction force and the swing of the hinged arm, avoiding tilting and deflection as much as possible, and the height of the saw blade 21 is more consistent with the cutting angle.

[0051] The limiting groove 42 is an arc groove. The first hinge point 35 between the first hinge arm 31 and the machine head 20 coincides with the center of the arc groove. The limiting groove 42 has a first end 43 and a second end 44 that are arranged opposite to each other along its extension direction. The machine head 20 has a first position away from the worktable 10 and a second position close to the worktable 10. When the machine head 20 is moved to the first position by an external force, the limiting pin 23 abuts against the first end 43 to keep the machine head 20 in the first position. When the machine head 20 is moved to the second position by an external force, the limiting pin 23 abuts against the second end 44 to keep the machine head 20 in the second position. This more accurately realizes the reliable switching between the two working positions of the machine head 20, which is raised for operation and pressed down for cutting. It can also achieve rigid limiting through hard contact after the machine head 20 reaches the target position, preventing the machine head 20 from being accidentally raised, lowered or shaken under the action of cutting vibration, its own weight or external force. This ensures that the machine head 20 can be more stably maintained in the set posture in both the raised standby and pressed down cutting states. When the saw head 20 is in the second position, the saw blade 21 can extend into the guide groove 131 and reciprocate, minimizing lateral movement of the saw blade 21. When the saw head 20 is in the second position, the limiting pin 23 abuts tightly against the end wall of the limiting groove 42, thus fixing the saw head 20 relative to the limiting plate 41; the two can be considered as a single unit. In this state, driven by the quadrilateral linkage mechanism, the limiting plate 41 and the saw head 20 will perform synchronous movements.

[0052] An elastic element 50 is provided between the first hinge arm 31 and the machine head 20. The two ends of the elastic element 50 act on the first hinge arm 31 and the machine head 20 respectively to apply an elastic restoring force to the machine head 20 to make it tend to the first position. Thus, when the machine head 20 is pressed down to the second position for cutting, the elastic element 50 stores elastic potential energy. After the cutting is completed and the external force is removed, the elastic restoring force automatically drives the machine head 20 to return to the first position. This realizes the automatic switching between pressing down and lifting the machine head 20 for cutting and returning to the first position. There is no need for manual lifting of the machine, making the operation more labor-saving and efficient.

[0053] It should be noted that, in addition to directly driving the machine head 20 back to the first position, the elastic element 50 can also be a smaller elastic element 50, so that it is only used to completely or partially offset the weight of the machine head 20, thereby helping the user to lift the machine head 20 more easily. Furthermore, the synchronous transmission element 30 includes a pin 301 disposed between adjacent articulated arms, a transmission shaft 302 disposed between adjacent pins 301, and bevel gears 303 disposed on the pins 301 and the transmission shaft 302. The bevel gears 303 on the pins 301 and the transmission shaft 302 mesh, and the linkage of each articulated arm is achieved through the meshing of the bevel gears 303. The length of the first hinge arm 31 is less than the length of the second hinge arm 32. By changing the gear ratio of the bevel gears 303 on the two hinge arms, for example, 1:1.2, when the second hinge arm 32 flips downward relative to the fixed part 11, under the action of the synchronous transmission member 30, the first hinge arm 31 flips upward relative to the second hinge arm 32. The height of the first hinge arm 31 and the first hinge point 35 of the machine head 20 is constant, thereby driving the machine head 20 to achieve a smooth horizontal movement at the same height as possible.

[0054] The pin 301 and the hinge arm, as well as the pin 301 and the bevel gear 303, are fixedly connected by elastic pins 304. The elastic pins 304 pass radially through the through holes aligned between the pin 301 and the hinge arm, and between the pin 301 and the bevel gear 303. They achieve self-locking by utilizing the radial elastic force generated by their own interference fit. The elastic pins 304 are easy to assemble and do not require complex fastening tools, which can quickly achieve a firm connection between the two.

[0055] The handle 24 is installed above or slightly behind the center of gravity of the head 20, conforming to the ergonomic grip angle, so that when the operator applies horizontal thrust, the line of action of the force passes through the center of mass of the head 20 as much as possible, reducing the tilting or jamming of the head 20 caused by torque imbalance. At the same time, the surface of the handle 24 is provided with anti-slip texture.

[0056] like Figure 6 As shown, in its free state, the saw head 20 is in the first position due to the elastic force of the elastic element 50, at which point the limiting pin 23 abuts against the first end 43. In use, the motor 22 is started, the saw blade 21 rotates, and by pressing down the handle 24, as shown... Figure 7 As shown, the machine head 20 is positioned in the second position, at which point the limiting pin 23 abuts against the second end 44. (See diagram) Figure 8As shown, the machine head 20 is then pulled horizontally in a straight line. The second hinge arm 32 flips downward relative to the fixed part 11. Under the action of the synchronous transmission member 30, the first hinge arm 31 flips upward relative to the second hinge arm 32, keeping the height of the first hinge arm 31 and the first hinge point 35 of the machine head 20 constant. At the same time, the posture holding linkage 40 pulls the limiting plate 41, causing the machine head 20 to rotate relative to the first hinge arm 31. This counteracts the angle at which the machine head 20 is raised as it follows the rotation of the first hinge arm 31, thus keeping the posture of the machine head 20 unchanged and ensuring that the saw blade 21 remains at a consistent height. The motor 22 is stopped after cutting is complete. The handle 24 can be pulled up manually, or the saw head 21 can be automatically reset by the elastic force of the elastic member 50. Figure 9 As shown, the head 20 is placed in the first position, and then the head 20 is pushed back to the initial position in the opposite direction.

[0057] Understandably, in other embodiments, the multiple articulated arms can also be three, four, or even more articulated arms, forming a multi-section series long-stroke translation mechanism. In such multi-section arm embodiments, the structure of the synchronous transmission component is expanded accordingly, including multiple series transmission shafts running through the interior of all adjacent articulated arms, and bevel gear sets set at the pins and corresponding transmission shaft ends at each articulation point. By designing the gear ratio and installation phase of each stage of bevel gears, a multi-level linkage constraint chain is constructed: when the first articulated arm rotates, the power is transmitted step by step through the transmission shaft and bevel gear set, forcing each subsequent articulated arm to produce a specific angle compensation relative to the previous articulated arm. This can offset the huge cumulative vertical displacement error that would originally occur after multiple articulated arms are connected in series, so that the connection point between the last articulated arm and the machine head still maintains horizontal linear movement on the spatial motion trajectory, thereby expanding the working stroke range of the equipment while maintaining the consistent saw blade height.

[0058] In addition to the preferred embodiments described above, the present invention has other embodiments. All other embodiments obtained by those skilled in the art based on the embodiments of the present invention without creative effort are within the scope of protection claimed by the present invention.

Claims

1. A single-set hinged miter saw, comprising a worktable (10) and a saw head (20), wherein a saw blade (21) is mounted on the saw head (20), and the saw head (20) is connected to the worktable (10) via a plurality of hinged arms, wherein a synchronous transmission member (30) is provided between the hinged arms to maintain a constant height at the first hinge point (35) between the hinged arms and the saw head (20), characterized in that, The articulated arm includes a first articulated arm (31) hinged to the machine head (20) and a second articulated arm (32) hinged to the first articulated arm (31). A posture-holding link (40) is also hinged between the second articulated arm (32) and the machine head (20). The distance from the second articulated arm (31), the posture-holding link (40), the second hinge point (36) between the first articulated arm (31) and the second articulated arm (32), to the third hinge point (36) between the posture-holding link (40) and the second articulated arm (32) is... The first link segment (33) between 7) and the second link segment (34) between the fourth hinge point (38) of the attitude holding link (40) and the head (20) and the first hinge point (35) of the first hinge arm (31) and the head (20) together constitute a quadrilateral link mechanism. When the first hinge arm (31) flips relative to the second hinge arm (32) and drives the head (20) to move laterally, the quadrilateral link mechanism constrains the head (20) to rotate in the opposite direction relative to the first hinge arm (31).

2. The single gang hinge type miter saw of claim 1, wherein, The lengths of the first link segment (33), the attitude holding link (40), the second link segment (34), and the first articulated arm (31) are different.

3. The single-set hinged miter saw according to claim 2, characterized in that, The length of the attitude-maintaining link (40) is greater than the length of the first articulated arm (31), and the length of the first link segment (33) is less than the length of the second link segment (34).

4. The single gang hinge style miter saw of claim 2, wherein, The length ratio of the first link segment (33), the attitude holding link (40), the second link segment (34) and the first articulated arm (31) is 10: (105~110): (20~24): (100~104).

5. The single group hinge type miter saw according to claim 1, wherein A limiting plate (41) is also fitted at the hinge shaft between the machine head (20) and the first hinge arm (31). A limiting groove (42) is provided on the limiting plate (41). A limiting pin (23) is fixed on the machine head (20). The limiting pin (23) extends into the limiting groove (42). When the limiting plate (41) rotates, the groove wall of the limiting groove (42) pushes against the end wall of the limiting pin (23) to drive the machine head (20) to rotate.

6. The single gang hinge type miter saw of claim 5, wherein, The attitude holding link (40) is hinged to the limiting plate (41) to achieve hinge on the head (20).

7. The single group hinge type miter saw according to claim 5, wherein The limiting groove (42) has a first end (43) and a second end (44) arranged opposite to each other along its extension direction. The machine head (20) has a first position away from the worktable (10) and a second position close to the worktable (10). When the machine head (20) is moved to the first position by an external force, the limiting pin (23) abuts against the first end (43) to keep the machine head (20) in the first position. When the machine head (20) is moved to the second position by an external force, the limiting pin (23) abuts against the second end (44) to keep the machine head (20) in the second position.

8. The single-hinged miter saw according to claim 7, characterized in that, An elastic element (50) is provided between the first articulated arm (31) and the machine head (20). The two ends of the elastic element (50) act on the first articulated arm (31) and the machine head (20) respectively to apply an elastic restoring force to the machine head (20) to make it tend to the first position.

9. The single group hinge type miter saw according to claim 1, wherein The multiple hinged arms are arranged in a unidirectional direction and hinged sequentially.

10. The single-group hinge-type miter saw of claim 1, wherein, The synchronous transmission component (30) includes a pin (301) disposed between adjacent hinge arms, a transmission shaft (302) disposed between adjacent pins (301), and bevel gears (303) disposed on the pins (301) and the transmission shaft (302), wherein the bevel gears (303) on the pins (301) and the bevel gears (303) on the transmission shaft (302) mesh.

Images