WO2023138500A1 - 一种齿轮副、齿轮防跳齿机构及电动剪钳式工具 - Google Patents

一种齿轮副、齿轮防跳齿机构及电动剪钳式工具 Download PDF

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Publication number
WO2023138500A1
WO2023138500A1 PCT/CN2023/072070 CN2023072070W WO2023138500A1 WO 2023138500 A1 WO2023138500 A1 WO 2023138500A1 CN 2023072070 W CN2023072070 W CN 2023072070W WO 2023138500 A1 WO2023138500 A1 WO 2023138500A1
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WO
WIPO (PCT)
Prior art keywords
gear
tooth
skipping
bracket
force
Prior art date
Application number
PCT/CN2023/072070
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English (en)
French (fr)
Inventor
吕一飞
Original Assignee
永康市擎匠科技有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from CN202210061807.0A external-priority patent/CN114607735A/zh
Priority claimed from CN202210693110.5A external-priority patent/CN114982496A/zh
Application filed by 永康市擎匠科技有限公司 filed Critical 永康市擎匠科技有限公司
Publication of WO2023138500A1 publication Critical patent/WO2023138500A1/zh

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Classifications

    • A—HUMAN NECESSITIES
    • A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
    • A01G—HORTICULTURE; CULTIVATION OF VEGETABLES, FLOWERS, RICE, FRUIT, VINES, HOPS OR SEAWEED; FORESTRY; WATERING
    • A01G3/00—Cutting implements specially adapted for horticultural purposes; Delimbing standing trees
    • A01G3/02—Secateurs; Flower or fruit shears
    • A01G3/033—Secateurs; Flower or fruit shears having motor-driven blades
    • A01G3/037—Secateurs; Flower or fruit shears having motor-driven blades the driving means being an electric motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
    • F16H1/12—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes

Definitions

  • the invention belongs to the technical field of gear transmission, and in particular relates to a gear pair, a gear anti-skipping mechanism and electric scissors and pliers tools.
  • Gear-driven opening and closing working tools are commonly used working tools, but because the opening and closing working tools need to withstand external forces during use to achieve functions such as cutting, therefore, excessive external force can easily cause the gears to slip under the action of force, resulting in tooth jumping, resulting in problems such as normal use of the tool. If the external force is too large, it will cause the problem of gear detachment, etc., that is, the passive side swing bevel gear of the existing electric scissors in the working mode is prone to slipping and jumping teeth when the shearing force is applied, so that the scissors cannot work.
  • the existing opening and closing tools are all set according to specifications.
  • One opening and closing tool can only meet the requirements of the same operation or the same specification, but cannot realize the requirements of universal design by quickly replacing opening and closing parts, such as shearing blades.
  • the Chinese patent document (announcement date: April 9, 2021, announcement number: CN212910875U) discloses a single-action blade electric scissors with anti-skipping function, which includes a bracket, a swing tooth rotatably mounted on the bracket, a movable blade mounted on the swing tooth and driven to rotate by the swing tooth, a fixed blade fixed on the bracket and adapted to the movable blade, and a bevel gear and a driving device for driving the swing tooth.
  • the anti-skip tooth screw, the end of the anti-skip tooth screw is exposed on the inner surface of the bracket, and forms a gap with the outer surface of the swing tooth.
  • the movable blade When cutting a branch with a large size, the movable blade will be deflected outward by a large normal force, so that the pendulum tooth will also be deflected outward to cause deformation. At this time, the outer surface of the pendulum tooth will be in contact with the end of the anti-skipping tooth screw to play a supporting role, preventing the pendulum tooth from failing when the deformation exceeds the meshing height of the bevel gear.
  • the above technical solution is to prevent tooth skipping by setting anti-skipping screws.
  • the technical solution is that the anti-skipping screws are point-type force-resistant anti-skipping teeth. When the movable blade is biased outward by a large normal force, the swing teeth are deflected outward. At this time, the anti-skipping screws support the swing teeth in a point-type manner, which will cause single-point force on the swing teeth.
  • the first object of the present invention is to solve the problem that the existing gear pair is easy to slip during the gear transmission process, resulting in tooth skipping, and the gear-driven scissors or pliers are easy to slip during use, resulting in tooth skipping.
  • Phenomenon affecting the normal use of the tool, while overcoming the existing single-point force on the anti-skip structure, uneven force, can not really solve the problem of anti-skip, and provide a gear pair, a bevel gear pair, through the tooth structure of the meshing teeth themselves to achieve meshing anti-skip teeth, so that the gear pair can always mesh and work during the working process without losing teeth.
  • the second object of the present invention is to provide a gear anti-skipping mechanism, through the tooth shape of the gear pair itself and the anti-skipping mechanism of the surface contact anti-skipping components alone or jointly, the swing teeth are evenly stressed, and the occurrence of tooth skipping can be effectively avoided.
  • an anti-skipping mechanism of the gear is provided, which can effectively prevent the phenomenon of bending deformation caused by the force on one side of the gear bracket, and prevent the phenomenon of tooth skipping during the shearing process.
  • the third object of the present invention is to provide an electric scissors and pliers tool that can quickly replace the opening and closing parts; and an electric shearing tool with balanced force to solve the problems that the gear bracket is prone to bending and deformation under the force of one side, and the bevel gear pair and the pendulum gear pair are separated from the gear contact to cause tooth jumping, etc.
  • the technical solution adopted by the present invention to achieve its first invention objective is: a gear pair, including a driving gear and a passive side swing gear meshing with each other.
  • the driving gear and the passive side swing gear are provided with an anti-skip tooth structure.
  • the anti-skip tooth structure is a tooth surface with a tooth surface angle of 75° to 90°.
  • the tooth surface is the shear force working surface when the passive side swing gear is oscillating.
  • the angle between the shear force working surface and the horizontal plane is 0 to 15°.
  • the tooth surface of the anti-skipping tooth is arranged on the driving gear and the driven gear.
  • the tooth surface is approximately a right-angled trapezoidal structure, so that the force direction of the passive side swing gear mainly acts on the tooth surface, which greatly reduces the outward normal force of the passive side swing gear, so that the passive side swing gear is not easy to slip and skip teeth, so that the shearing force of the passive side swing gear always faces the direction of meshing with the driving gear. Thereby, the risk of gear slippage is reduced, and the problem of tooth skipping of passive side swing gears is completely solved.
  • the driving gear is a driving bevel gear, and the driving gear includes a spiral bevel gear and a straight bevel gear;
  • the passive side swing gear is a driven side swing bevel gear, and the passive side swing gear includes a spiral bevel gear and a straight bevel gear.
  • the technical solution adopted by the present invention to realize its second invention objective is: a gear anti-skipping mechanism with a gear pair, including a gear bracket, a fixed assembly and a moving assembly arranged on the gear bracket and opened and closed through the gear pair meshing, and the tooth surface forming the anti-skipping structure on the passive side swing gear is the shear force working surface of the moving assembly in the direction of closing.
  • the gear anti-skipping mechanism is provided with an anti-skipping structure on the gear pair.
  • the anti-skipping structure makes the passive side swing gear mesh with the driving gear and receives shear force. Reduced, that is, the force of disengagement is effectively reduced, thereby reducing the risk of gear slippage, and completely solving the problem of tooth skipping of passive side swing gears.
  • the tooth configuration of the passive side swing bevel gear is approximately a right-angled trapezoidal structure, and its approximately right-angled tooth surface is set as the shear force working surface when the shearing moving component moves towards the closing direction.
  • the angle between the shearing force working surface and the horizontal plane is between 0 and 15 degrees, so that the force direction of the passive side swing gear mainly acts on the moving component, which greatly reduces the outward normal force of the passive side swing gear and makes it difficult for the passive side swing gear to slip.
  • this angle range can be relaxed when the shearing force is small.
  • the driving gear is also provided with a tooth surface in an approximately right-angled trapezoidal structure to be paired with the driven side swing gear to mesh with each other.
  • an anti-skipping component is provided on the outside of the passive side swing gear, and a gap is provided between the inner surface of the anti-skipping gear component and the outer surface of the passive side swing gear; the anti-skipping tooth component and the gear bracket form a symmetrical force-bearing structure.
  • An anti-skipping component is installed on the outside of the passive side swing gear, and double anti-skipping teeth are realized through the anti-skipping tooth structure and the anti-skipping tooth component.
  • the anti-skipping tooth component makes the passive side swing gear between the gear bracket and the anti-skipping tooth component.
  • the gear bracket and the anti-skipping tooth component form a symmetrical force structure on both sides, which avoids the problem of bending deformation of the gear bracket under unilateral force during the shearing process and improves the shearing stability.
  • the gap enables the outer surface of the passive side swing gear to fit with the inner surface of the anti-skipping component, and prevents the occurrence of the outward deformation of the passive side swing gear due to the surface-to-surface fit.
  • the anti-skipping gear part includes a gear bracket connection end and a rotating shaft connecting end integrally arranged, a shaft hole is arranged at the shaft connecting end, and a plurality of fixing holes are provided at the gear bracket connecting end; the rotating shaft connecting end of the anti-jumping gear part and the driven side swing gear contact through a plane or a plane thrust bearing; a gap is provided between the inner surface of the gear bracket connecting end of the anti-jumping gear part and the outer surface of the driven side swing gear.
  • the anti-skipping component is preferably a symmetrical force anti-skipping link.
  • the above-mentioned structure of the anti-skipping component is convenient to connect with the rotating shaft through the shaft hole, so as to realize the coaxial arrangement with the passive side swing gear and the moving assembly. design. And the gap between the outer surface of the passive side swing gear and the inner surface of the anti-jumping gear component is small enough, and the size of each part can be set in this gap generally during processing, and the installation dimensions of different opening and closing components are corresponding.
  • the driving gear is a driving bevel gear
  • the driving gear includes a spiral bevel gear and a straight bevel gear.
  • the driving gear is installed on the gear bracket and connected with the power mechanism in a force transmission manner, and the moving assembly is connected with the driven side swing gear and is rotatably connected with the gear bracket through a rotating shaft.
  • the passive side swing gear is a passive side swing bevel gear
  • the passive side swing gear includes a spiral bevel gear and a straight bevel gear
  • the passive side swing gear is provided with a swing bar structure with a gear end and a swing end, and the gear end meshes with the driving gear.
  • the fixed assembly is provided with a gear bracket fixing hole and a rotating shaft hole;
  • the moving assembly is provided with a rotating shaft hole and a fixing pin hole.
  • the setting of the gear bracket fixing hole on the fixed component is for the convenience of the fixed connection between the fixed component and the gear bracket, and the setting of the rotating shaft hole is for the convenience of the fixed component and the rotating shaft threaded fixed connection.
  • the rotating shaft hole is provided on the moving assembly to facilitate the rotation connection with the rotating shaft, and the fixed pin hole is for facilitating the connection of the moving assembly with the passive side swing gear through connection.
  • the gear bracket includes a connecting body and an installing body integrally arranged.
  • the above-mentioned structure of the gear bracket can be connected with the motor and the reducer housing through the connecting body.
  • the installation of the driving gear, the fixed assembly, the moving assembly and the anti-skipping component can be realized through the mounting body.
  • the combination of the gear bracket and the anti-skipping component can form a symmetrical force structure.
  • the rotating shaft structure is designed according to the coaxial structure of the gear bracket, the fixed assembly, the moving assembly, the passive side swing gear and the anti-skipping component, including the penetrating structure from the side of the gear bracket and the penetrating structure from the side of the anti-skipping component.
  • the passive side swing gear can be arranged on the left or right side of the gear bracket
  • the anti-skipping parts are correspondingly arranged on the left side and the right side
  • the rotating shaft is also correspondingly penetrated from the right side and the left side to realize the connection. Therefore, the rotating shaft can be set in different structural shapes, and the specific operation is set according to actual needs.
  • the technical solution adopted by the present invention to realize its third invention objective is: an electric scissors tool, including a motor, a reducer and the gear anti-skipping mechanism.
  • the motor is connected to a reducer
  • the reducer is connected to the gear bracket and the driving gear and transmits the output torque to the driving gear
  • the driving gear transmits the torque to the passive side swing gear
  • the passive side swing gear drives the fixed assembly to realize opening and closing.
  • the electric scissors tool includes a motor, a reducer, a fixed assembly and a moving assembly arranged inside the casing.
  • the motor is connected to the reducer, the reducer is connected to the driving gear and transmits output torque, the driving gear transmits the torque to the passive side swing gear, and the moving assembly connected to the passive side swing gear and it is opened and closed with the rotating shaft as the center of rotation.
  • the moving assembly and the fixed assembly form a shearing mode or a pliers mode. It is fastened by fastening nuts and anti-loosening screws to form opening and closing tools such as electric scissors or electric pliers.
  • the electric scissors tool due to the anti-jump tooth structure or the The double anti-skipping mechanism of the anti-skipping structure and anti-skipping components completely solves the problem of the passive side swing gear skipping teeth, making it always mesh with the driving gear without slipping and skipping teeth, ensuring normal opening and closing work.
  • a bevel gear pair comprising an active bevel gear and a passive bevel gear meshing with each other, the active bevel gear and the driven bevel gear respectively comprising a spiral bevel gear and a straight bevel gear;
  • the tooth shape of the bevel gear pair is set in a right-angled trapezoidal force-bearing structure, and the bevel tooth shape of the driven gear is set in a tooth-shaped structure close to a right-angled trapezoid.
  • the included angle with the horizontal plane is 0-15 degrees.
  • a gear anti-skipping mechanism with a bevel gear pair including a gear bracket, a shearing assembly arranged on the gear bracket and opened and closed by the gear pair meshing, and an anti-skipping component is arranged outside the shearing assembly; the gear bracket and the anti-skipping component form a symmetrical force-bearing structure.
  • the bevel gear pair is arranged on the gear bracket through a pinion
  • the shear assembly is set on the gear bracket through a rotating shaft
  • the symmetrical force-bearing structure forms a symmetrical balanced force-bearing structure with the gear shaft and the rotating shaft.
  • the symmetrical balanced force-bearing structure is arranged in a well-shaped structure; the gear shaft and the rotating shaft constitute a double-stressed support beam for opening and closing the shear force of the shearing assembly, and the gear bracket and the anti-skipping parts constitute a double-beam frame structure for limiting balanced force on both sides of the shearing assembly and preventing tooth loss.
  • the symmetrical balanced force structure consists of gear brackets and anti-skipping parts arranged in the axial direction, along with the gear shafts and rotating shafts perpendicular to the gear brackets and anti-jumping parts to form a well structure.
  • a balanced force electric shearing tool including the gear anti-skipping mechanism, and also includes a power assembly
  • the power assembly includes a motor and a planetary reducer.
  • the power component is equipped with a motor and a planetary reducer, the motor transmits power to the active bevel gear, the active bevel gear transmits power to the passive bevel gear, and the passive bevel gear drives the gear shaft to rotate, thereby transmitting the power to the shearing component to achieve shearing.
  • the balanced force electric shearing tool forms a balanced force-bearing structure through a gear bracket, an anti-skipping component, a gear shaft and a rotating shaft (that is, the cutter shaft), so that during the shearing process of the shearing component, the force generated during the shearing process will be transmitted to both sides of the gear bracket and the anti-skipping component in a balanced manner, effectively preventing the occurrence of bending deformation caused by one-sided force on the gear bracket.
  • the shearing assembly is supported by two front and rear beams, which makes the shearing operation more stable.
  • the anti-jump gear component is a balance link bridge, and the two ends of the balance link bridge are respectively provided with gear shaft connection holes and cutter shaft connection holes.
  • the balanced connecting rod bridge takes the connecting rod structure as the preferred solution.
  • gear shaft connection holes and cutter shaft connection holes at the front and rear to form a bridge-type force-bearing structure, which prevents the shearing component from slipping outward due to force and tooth loss, and also avoids the occurrence of bending deformation caused by unilateral force on the gear bracket.
  • the shearing assembly includes a dynamic shearing assembly and a fixed shearing assembly
  • the fixed shearing assembly includes a fixed knife fixing part and a fixed blade
  • the fixed knife fixing part is connected to a gear bracket
  • the moving shearing assembly includes swing teeth and a moving blade
  • the swing teeth mesh with the gear shaft to drive the moving blade to open and close to form a shearing structure with the fixed shearing set.
  • the shearing assembly includes a dynamic shearing assembly and a fixed shearing assembly.
  • the fixed shearing assembly includes a fixed blade and a fixed blade fixing part.
  • the fixed blade fixing part is used to realize a fixed connection with the gear bracket so that the fixed blade is fixed relative to the gear bracket.
  • the dynamic shearing assembly includes a swinging tooth and a moving blade meshing with the gear shaft.
  • the swing tooth and the movable blade are of a split structure, and the movable blade and the swing tooth are fixedly connected by fasteners; the swing tooth is provided with a center hole of the swing tooth, and the movable blade is provided with a center hole of the movable knife, and the center hole of the swing tooth and the center hole of the movable knife are arranged coaxially.
  • the swing tooth and the moving blade are set as a split structure, the swing tooth meshes with the gear shaft, and the moving blade is fixedly connected to the swing tooth.
  • the center hole of the swing tooth is set on the swing tooth to facilitate the coaxial connection between the swing tooth and the moving blade and the cutter shaft, so that the swing tooth and the moving blade rotate with the cutter shaft as the center, and then form a shearing mode with the fixed blade, which also realizes the double-beam support force structure of the shearing component.
  • the swing tooth and the movable blade are of an integral structure, and a cutter shaft installation hole is provided at the middle of the integral swing tooth and the movable blade.
  • the oscillating gear and the movable blade are arranged in an integrated structure, the end of the oscillating gear meshes with the gear shaft, and the end of the movable blade cooperates with the fixed blade to form a shearing structure.
  • Such a dynamic shearing assembly is easier to set up, and can also realize the setting of an elongated blade. It is more convenient to design changes in the center distance between the gear shaft and the cutter shaft.
  • the gear bracket has an integrated bracket structure, and the end of the gear bracket close to the power assembly is provided with a gear shaft installation hole, and the axis of the gear shaft installation hole is set perpendicular to the output axis of the power assembly or coaxially with the output axis of the power assembly; the end of the gear bracket away from the power assembly is provided with a cutter shaft installation hole Or be provided with fixed blade fastening upper hole and fixed blade fastening lower hole.
  • the gear bracket is provided with an integrated bracket structure, the motor is connected to the planetary reducer, and the planetary reducer is connected to the gear transmission assembly, and the gear transmission assembly is connected to the pinion shaft. Therefore, a gear shaft mounting hole is provided on the gear bracket.
  • a knife shaft mounting hole is provided at the other end of the gear bracket, so as to facilitate the installation of the knife shaft, and then form a double force supporting beam structure.
  • the other end of the gear bracket is provided with an upper hole for fastening the fixed blade and a lower hole for fastening the fixed blade, so that the fixed shear component can be directly fixedly connected with the gear bracket.
  • the gear shaft installation hole on the gear bracket is arranged coaxially with the output shaft of the power assembly, that is to say, the planetary reducer and the gear shaft are coaxially transmitted.
  • the split housing structure of the gear bracket includes a right housing with a right space and a left housing with a left space, and the shear assembly is arranged between the right housing and the left housing.
  • the gear bracket can also be a split shell structure, that is, the gear bracket and the shell of the shearing tool can be made into an integrated structure, specifically, it includes a left shell and a right shell, and the left shell and the right shell have a left space and a right space respectively, which are used for the shearing activity space after the shearing assembly is installed.
  • Such a structure can also form a left-right symmetrical structure with the balance connecting rod bridge, and form a well-shaped symmetrical balanced force-bearing structure with the gear shaft and the cutter shaft.
  • the gear pair and the gear anti-skipping mechanism of the present invention completely solve the problem of gear skipping.
  • the anti-skipping structure makes the passive side swing gear mesh with the driving gear and receives shear force. Effective reduction, that is, the disengagement force is effectively reduced, thereby reducing the risk of gear slippage and completely solving the problem of tooth skipping of passive side swing gears.
  • the anti-skipping component and the gear bracket form a U-shaped symmetrical force-bearing structure, which prevents the gear bracket from bending and deforming under unilateral force.
  • the gap between the anti-skipping component and the outside of the passive side-sway gear is small enough to block the passive side-sway gear when it exceeds the external force. Relevant workers have maintenance troubles caused by the failure of scissors and pliers to work due to the jumping teeth of opening and closing tools.
  • the bevel gear pair and the balanced force electric shearing tool in the present invention greatly reduce the force on the shearing assembly, causing the shearing assembly and the gear shaft to deviate in the opposite direction, causing the gear bracket to bend and deform, thereby preventing the gear transmission assembly from deviating from the meshing direction, making it difficult for the gear transmission assembly and the shearing assembly to slip.
  • the risk of wheel slippage is completely solved, and the problem that the gear bracket is easily bent and deformed by the force, and the gear transmission component and the shearing component slip and skip teeth is completely solved.
  • the shearing assembly is supported by two front and rear beams, which makes the shearing operation more stable.
  • the entire shearing tool is balanced in front, rear, left, and right, and the operation is more stable and the service life is longer.
  • Fig. 1 is a kind of structural representation of gear pair of the present invention
  • Fig. 2 is a kind of structural representation of anti-jump tooth structure of the present invention
  • Fig. 3 is another kind of structural representation of anti-jump tooth structure in the present invention.
  • Fig. 4 is a schematic diagram of an exploded structure of the gear anti-skipping mechanism of the present invention.
  • Fig. 5 is a schematic structural view of the gear anti-skipping mechanism in Embodiment 3 of the present invention.
  • Fig. 6 is a schematic structural view of the anti-jumping tooth component in the present invention.
  • Fig. 7 is a kind of structural representation of electric scissors opening and closing state in the present invention.
  • Fig. 8 is a schematic diagram of an exploded structure of electric scissors in Embodiment 4 of the present invention.
  • Fig. 9 is a schematic structural view of the tooth shape of the bevel gear pair in Embodiment 5 of the present invention.
  • Fig. 10 is a schematic structural diagram of an open state of a balanced force electric shearing tool in Embodiment 6 of the present invention.
  • Fig. 11 is a schematic diagram of the exploded structure of the electric shearing tool with balanced force in Embodiment 7 of the present invention.
  • Fig. 12 is a schematic structural diagram of a balanced force electric shearing tool in Embodiment 8 of the present invention.
  • Fig. 13 is a schematic structural view of a balanced force electric shearing tool in Embodiment 9 of the present invention.
  • Fig. 14 is a schematic structural view of a balanced force electric shearing tool in Embodiment 10 of the present invention.
  • Fig. 15 is a structural schematic diagram of a balanced force electric shearing tool after the center distance between the gear shaft and the cutter shaft is increased in the present invention
  • Fig. 16 is a schematic structural view of a balanced force electric shearing tool in Embodiment 11 of the present invention.
  • a gear pair includes a driving gear 4 and a passive side swing gear 5 meshing with each other.
  • the driving gear 4 and the passive side swing gear 5 are provided with an anti-skip tooth structure, and the anti-skip tooth structure is a tooth surface 57 with a tooth surface angle ⁇ of 75 degrees to 90 degrees. degree.
  • Described driving gear 4 is driving bevel gear, and described driving gear 4 comprises spiral bevel gear and straight bevel gear;
  • Described passive side swing gear 5 is passive side swing bevel gear, and described passive side swing gear 5 comprises spiral bevel gear and straight bevel gear.
  • the passive side swing gear 5 is provided with a tooth surface 57 with a tooth surface angle ⁇ of 75° to 90°, the tooth surface 57 is the shear force surface when the passive side swing gear oscillates and engages, and the angle ⁇ between the working surface of the shear force surface and the horizontal plane is 0° to 15°.
  • the tooth configuration of the passive side swing bevel gear is approximately a right-angled trapezoidal structure, and its approximately right-angled tooth surface is set as the shearing force surface during the swing meshing.
  • the angle ⁇ between the shearing force working surface and the horizontal plane is between 0 and 15 degrees.
  • the tooth surface angle ⁇ is 75 degrees, and the shearing force working surface angle ⁇ is close to the horizontal plane.
  • the angle ⁇ of the tooth surface is 80 degrees, and the angle ⁇ of the working surface under shear force is close to the horizontal plane by 10 degrees.
  • the tooth surface of the corresponding driving gear is paired and meshed with the driven side swing gear.
  • a gear anti-skipping mechanism is suitable for various opening and closing tools in various industries that require opening and closing actions. It includes a gear bracket 3, a gear pair assembly, a fixed assembly 1 and a moving assembly 2 that are arranged on the gear bracket 3 and are opened and closed through the gear pair assembly.
  • the gear pair assembly includes a driving gear 4 and a passive side swing gear 5 that meshes with the driving gear 4.
  • the bracket 3 is rotatably connected, and the gear pair assembly is provided with an anti-skip tooth structure.
  • the anti-skip tooth structure is a tooth surface 57 with a tooth surface angle ⁇ of 75 degrees to 90 degrees.
  • the direction is the shear force working surface, and the angle ⁇ between the shear force working surface and the horizontal plane is 0 to 15 degrees.
  • the force direction of the passive side swing gear 5 mainly acts on the moving assembly, greatly reducing the outward normal force of the passive side swing gear 5 so that the passive side swing gear 5 is not easy to slip and skip teeth.
  • the passive side swing gear 5 is provided with a tooth surface 57 with a tooth surface angle ⁇ of 75° to 90°, the tooth surface 57 is the shear force surface when the moving assembly moves toward the closing direction, and the angle ⁇ between the shear force surface working surface and the horizontal plane is 0° to 15°.
  • the tooth configuration of the passive side swing bevel gear is approximately a right-angled trapezoidal structure, and its approximately right-angled tooth surface is set as the shearing force surface when the shearing moving component moves toward the closing direction.
  • the angle ⁇ between the shearing force working surface and the horizontal plane is between 0 and 15 degrees.
  • the tooth surface angle ⁇ is 75 degrees, and the shearing force working surface angle ⁇ is close to the horizontal plane.
  • the passive side swing gear 5 is not easy to slip and skip teeth; of course, this angle range can be relaxed when the shearing force F is small.
  • the angle ⁇ of the tooth surface is 80 degrees, and the angle ⁇ of the working surface under shear force is close to the horizontal plane by 10 degrees.
  • the tooth surface of the corresponding driving gear is paired and meshed with the driven side swing gear.
  • a gear anti-skipping mechanism is suitable for opening and closing tools in various industries that require opening and closing actions. It includes a gear bracket 3 , a gear pair assembly, a fixed assembly 1 and a moving assembly 2 that are arranged on the gear bracket 3 and engage with the gear pair assembly.
  • the gear pair assembly includes a driving gear 4 and a passive side swing gear 5 meshing with the driving gear 4 .
  • the gear pair assembly is provided with an anti-skip tooth structure, and an anti-skip tooth part 7 is arranged on the outside of the passive side swing gear 5, and there is a gap between the inner side of the anti-skip tooth part 7 and the outer side of the passive side swing gear 5; the anti-skip tooth part 7 and the gear bracket 3 form a symmetrical force-bearing structure.
  • the anti-jumping tooth structure is a tooth surface 57 with a tooth surface angle ⁇ of 75° to 90°.
  • the tooth surface is the shear force surface when the moving assembly moves toward the closing direction, and the angle ⁇ between the shear force surface working surface and the horizontal plane is 0 to 15°.
  • the force direction of the passive side swing gear 5 mainly acts on the moving assembly, greatly reducing the outward normal force of the passive side swing gear 5 so that the passive side swing gear 5 is not easy to slip and skip teeth;
  • the anti-jumping gear component in this embodiment is a symmetrically stressed anti-jumping gear connecting rod.
  • the anti-jumping gear component 7 includes a gear bracket connection end 71 and a shaft connection end 72 that are integrally provided.
  • a shaft hole 73 is provided at the shaft connection end 72, and a plurality of fixing holes 75 are provided at the gear bracket connection end 71.
  • the connecting end of the rotating shaft of the anti-skipping component 7 and the driven side swing gear contact through plane contact or contact through a plane thrust bearing; in this embodiment, contact through a plane thrust bearing 8 is preferred.
  • the anti-jumping parts By setting the anti-jumping parts to form a U-shaped symmetrical force structure with the gear bracket, the anti-jumping parts in this embodiment
  • the connecting end of the gear bracket is set in a T-shaped structure
  • the connecting end of the rotating shaft is set in a circular shape, which is convenient to connect with the rotating shaft through the shaft hole, so as to realize the coaxial setting with the passive side swing gear and the moving component. Replacement of certain components in order to achieve the design of the universal structure.
  • the driving gear 4 is a driving bevel gear
  • the gear pair of the driving gear 4 includes a spiral bevel gear and a straight bevel gear.
  • the driving gear 4 is installed on the gear bracket 3 and is connected with the power mechanism in force transmission.
  • the passive side swing gear 5 is a passive side swing bevel gear, and the gear pair of the passive side swing gear 5 includes a spiral bevel gear and a straight bevel gear.
  • the passive side swing gear 5 has a swing rod structure and is provided with a gear end 51 and a swing end 52 , and the gear end 51 meshes with the driving gear 4 .
  • the passive side swing gear 5 is provided with a tooth surface 57 with a tooth surface angle ⁇ of 75° to 90°, the tooth surface 57 is the shear force surface when the moving assembly moves toward the closing direction, and the angle ⁇ between the shear force surface working surface and the horizontal plane is 0° to 15°.
  • the tooth configuration of the passive side swing bevel gear is approximately a right-angled trapezoidal structure, and its approximately right-angled tooth surface is set as the shearing force surface when the shearing moving component moves toward the closing direction.
  • the angle ⁇ between the shearing force working surface and the horizontal plane is between 0 and 15 degrees.
  • the tooth surface angle ⁇ is 75 degrees, and the shearing force working surface angle ⁇ is close to the horizontal plane.
  • the passive side swing gear 5 is not easy to slip and skip teeth; of course, this angle range can be relaxed when the shearing force F is small.
  • the angle ⁇ of the tooth surface is 80 degrees, and the angle ⁇ of the working surface under shear force is close to the horizontal plane by 10 degrees.
  • the tooth surface of the corresponding driving gear is paired and meshed with the driven side swing gear.
  • the fixed assembly 1 is provided with a gear bracket fixing hole 11 and a rotating shaft hole 12 ;
  • the moving assembly 2 is provided with a rotating shaft hole 21 and a fixing pin hole 22 .
  • the setting of the gear bracket fixing hole on the fixed component is for the convenience of the fixed connection between the fixed component and the gear bracket, and the setting of the rotating shaft hole is for the convenience of the fixed component and the rotating shaft threaded fixed connection.
  • the rotating shaft hole is provided on the moving assembly to facilitate the rotation connection with the rotating shaft, and the fixed pin hole is for facilitating the connection of the moving assembly with the passive side swing gear through connection.
  • the gear bracket 3 includes a connecting body 31 and a mounting body 32 integrally arranged.
  • the gear bracket can be connected with the motor and the reducer housing through the connecting body.
  • the installation of the driving gear, the fixed assembly, the moving assembly and the anti-skipping component can be realized through the mounting body.
  • the combination of the gear bracket and the anti-skipping component can form a symmetrical force-bearing structure, and the mounting body can be installed on the left or right side along the axis of the connecting body, that is, the anti-skipping component can be installed on the left or right side of the gear bracket in the direction of use.
  • the structure of the rotating shaft 6 is based on the structure of the gear bracket, the fixed assembly, the moving assembly, the passive side swing gear and the anti-skipping parts. Designed for the coaxial structure, including the penetrating structure from the side of the gear bracket and the penetrating structure from the side of the anti-skipping component. Since the passive side swing gear can be arranged on the left or right side of the gear bracket, the anti-skipping parts are correspondingly arranged on the left side and the right side, and the rotating shaft is also correspondingly penetrated from the right side and the left side to realize the connection. Therefore, the rotating shaft can be set in different structural shapes, and the specific operation is set according to actual needs.
  • the rotating shaft 6 adopts a penetrating structure from the side of the gear bracket.
  • the rotating shaft 6 penetrates from the direction of the gear bracket, passes through the gear bracket, fixed blade, moving blade, passive side swing bevel gear, plane thrust bearing and anti-skipping parts, and then locks it with nut 6 and screws.
  • the rotating shaft 6 includes an operating end 63, an outer circle of the shaft K6, an external thread of the rotating shaft F6, a rotating section 64 and a fastening section 65.
  • the outer circle of the rotating shaft K6 passes through the shaft hole 38 on the gear bracket and cooperates with it.
  • the symmetric force unilateral gear anti-skipping mechanism includes a gear bracket 3, a fixed knife assembly 1 is a fixed blade, a moving knife assembly 2 is a moving blade, a passive side swing gear is a passive side swing bevel gear, driving gear 4 is an active bevel gear, and a shaft 6 is a knife shaft; the active bevel gear meshes with the passive side swing bevel gear. As the center of rotation, it opens and closes and swings to form a shearing mode with the fixed blade.
  • the internal thread of the cutter shaft and the fixed blade fastens the gear bracket in the middle, and at the same time, the movable blade, the passive side swing bevel gear, the plane thrust bearing and the anti-skipping parts pass through the cutter shaft and are fastened by fastening nuts and anti-loosening screws.
  • the passive side swing bevel gear is installed between the gear bracket and the anti-skipping gear part.
  • the outer surface of the passive side swing bevel gear is provided with an anti-skipping gear part 7 connecting the gear bracket and the cutter shaft.
  • the function of the anti-skipping gear part is to prevent the gear bracket from bending and deforming under unilateral force.
  • the meshing of bevel gears completely solves the problem of tooth skipping of passive side swing bevel gears.
  • the gear bracket connecting end 71 of the anti-jumping tooth part 7 is fastened on the gear bracket 3 by bolts and nuts arranged in the fixing hole 75.
  • the number of bolts is set according to the size of the shearing force. For example, cutting objects such as branches with a smaller diameter can also reduce the number of nuts and bolts; the connecting end 72 of the rotating shaft is connected with the cutter shaft through the shaft hole 73, and is fastened by nuts and anti-loosening screws; the plane connection between the passive side swing bevel gear and the anti-jumping tooth part or by setting a plane thrust bearing 8 is realized in this embodiment. The connection is realized by means of a plane thrust bearing 8 .
  • the passive side-sway bevel gear can be directly used in plane contact with the anti-skipping component.
  • a trigger 343 and a spring 344 are also provided in another embodiment, and the trigger and spring can be arranged on the gear bracket or on the housing.
  • the passive side swing gear, the fixed assembly and the moving assembly can be installed and used on the left side or the right side of the scissors.
  • an electric scissors includes a motor 100, a reducer 200 and the gear anti-skipping mechanism described in the above embodiments.
  • the motor 100 is connected to the reducer 200
  • the reducer 200 is connected to the gear bracket 3 and the driving gear and transmits the output torque to the driving gear
  • the driving gear transmits the torque to the passive side swing gear
  • the passive side swing gear drives the fixed assembly to realize opening and closing.
  • the opening and closing of the moving knife of the scissors is formed by the positive and negative rotation of the driving bevel gear driven by the reducer and the motor.
  • the anti-skipping mechanism described in the above embodiment is provided with an anti-skipping structure on the gear subassembly.
  • the anti-skipping structure makes the passive side swing gear mesh with the driving gear and receives shear force. The meshing force is effectively reduced, thereby reducing the risk of gear slippage and completely solving the problem of tooth skipping of passive side swing gears.
  • an anti-skipping structure is provided on the gear pair assembly and an anti-skipping component is installed outside the passive side swing gear, and double anti-skipping teeth are realized through the anti-skipping tooth structure and the anti-skipping tooth component.
  • the gear bracket and the anti-skipping tooth parts form a symmetrical force structure on both sides, which avoids the problem of unilateral force on the gear bracket during cutting or clamping, avoids the problem of bending deformation of the gear bracket under unilateral force, and improves the stability of shearing or clamping; and there is a gap between the outer surface of the passive side swing gear and the inner surface of the anti-skipping tooth component, and the gap between the inner surface of the anti-skipping tooth component and the outer surface of the passive side swing gear is kept small enough, which will not affect the opening and closing of the driven component driven by the passive side swing gear.
  • the component can block the passive side swing gear when it is sheared and stressed, so that it is always meshed with the driving gear, without slipping and jumping teeth, and ensuring normal opening and closing work.
  • This electric scissors-type tool directly solves the maintenance troubles of fruit farmers, garden pruning, construction (PVC plastic) water pipe cutting, pliers operations and other related workers due to scissors and pliers opening and closing tools that cannot work due to tooth jumping.
  • Change the scope of use of the tool by replacing the fixed and/or moving components. For example, if it is set as a fixed blade, the moving blade can be assembled into electric scissors. Changing the fixed blade can change the electric scissors into an electric cutter for building and installing PVC plastic water pipes. It can also be a variety of other opening and closing tools for various industries that require opening and closing actions. For example, change to pliers or animal ear marking fixtures, branch grafting Tools for opening and closing actions such as fixtures.
  • a bevel gear pair includes a driving bevel gear P and a driven bevel gear 3' that are meshed with each other.
  • the driving bevel gear P and the driven bevel gear 3' include a spiral bevel gear and a straight bevel gear respectively;
  • the angle between the faces is 0-15 degrees.
  • the bevel gear pair tooth shape is a right-angled trapezoidal right-angled surface, and the bevel tooth shape of the driven wheel presents a tooth shape approximately close to a right-angled trapezoid.
  • the tooth surface that is approximately right-angled is the shearing force surface when the scissors are closed, and the angle of the shearing force working surface is close to the horizontal plane. In order to prevent the bevel teeth from slipping due to force jumping.
  • Embodiment 6 is a diagrammatic representation of Embodiment 6
  • a gear anti-skipping mechanism with a bevel gear pair includes a gear bracket 3, a shearing assembly arranged on the gear bracket 3 and opened and closed through the gear pair meshing, and an anti-skipping component 7 is arranged outside the shearing assembly; the gear bracket 3 and the anti-skipping component 7 form a symmetrical force-bearing structure.
  • the anti-jump tooth component 7 is a balance link bridge 17 .
  • Described bevel gear pair is arranged on the gear support 3 by a tooth shaft 19, and described shearing assembly is arranged on the gear support 3 by a rotating shaft 6 (being cutter shaft), and described symmetrical force structure forms symmetrical balance force structure with gear shaft 19 and rotating shaft 6 (cutter shaft); Described symmetrical balance force structure is the well structure arrangement; Described tooth shaft 19 and rotating shaft 6 (knife shaft) constitute the double stressed support beam of shearing assembly opening and closing shearing force, and described gear support 3 and anti-jump tooth part 7 constitute shearing assembly Double-beam frame structure with limit balance on both sides and anti-loosening teeth.
  • Embodiment 7 is a diagrammatic representation of Embodiment 7:
  • a balanced force electric shearing tool includes a power assembly, a gear transmission assembly and a shearing assembly.
  • the power assembly includes a motor 100 and a planetary reducer 2', the motor 100 is connected to the planetary reducer 2', the gear transmission assembly includes a driving bevel gear P and a passive bevel gear 3', the cutting assembly includes a moving knife assembly and a fixed knife assembly, and the fixed knife assembly includes a fixed knife fixing part and a fixed blade 9'.
  • the fixed knife fixing part is connected to the gear bracket 3, and the moving knife
  • the assembly includes a swing tooth 12' and a movable blade 11'.
  • the swing tooth meshes with the gear shaft to drive the movable blade to open and close to form a shearing structure with the fixed knife assembly. It also includes a gear bracket 3 and an anti-skipping component 7 , and in this embodiment, the anti-skipping component 7 is a balance link bridge 17 .
  • the movable blade 11' and the swing tooth 12' are arranged in a split structure and are fixedly connected by a knife pin 13' and a retaining spring 10'.
  • the movable blade 11' and the swing tooth 12' may also adopt an integral design structure.
  • a trigger spring 344 and a trigger 343 are also provided on the gear bracket 3 or on the shell of the shearing tool for realizing the operation of the shearing tool.
  • the planetary reducer 2' is connected to the active bevel gear P.
  • the active bevel gear P is supported and installed in the gear bracket 3 by the gear bearing M, the anti-retraction retaining spring C, and the retaining spring C1.
  • the passive bevel gear 3' is fixedly connected with the pinion shaft 19 and meshes with the active bevel gear P.
  • the active bevel gear P transmits the power engagement to the passive bevel gear 3'.
  • the anti-retraction snap spring C restricts the gear bearing M in the axial direction.
  • the pinion shaft 19 is passed through the gear bracket 3, and the pinion shaft 19 meshes with the swing tooth 12' and transmits power to the swing tooth 12'.
  • the swing tooth 12' includes a tooth end and a swing end, and a swing tooth center hole 12'A is arranged at the swing end of the swing tooth.
  • the end of the gear bracket 3 close to the planetary reducer is provided with a gear shaft installation hole 3A perpendicular to the axial direction of the planetary reducer, and the end of the gear bracket 3 away from the planetary reducer is provided with a cutter shaft installation hole 3F, and the axes of the cutter shaft installation hole 3F and the gear shaft installation hole 3A are parallel to each other.
  • Both ends of the balance link bridge 17 are respectively provided with a pinion shaft connection hole 17A and a cutter shaft connection hole 17F.
  • the center distance between the gear shaft connection hole 17A and the cutter shaft connection hole 17F on the balance link bridge 17 can be increased as required.
  • the corresponding replacement of the elongated movable blade and the fixed blade can form a cutting tool for branches with a larger diameter.
  • the elongated movable blade can be provided in an integral structure, or can be a separate structure of the movable blade 11 ′ and the swing tooth 12 ′ as shown in FIG. 11 .
  • the fixed blade 9' is provided with a fixed knife center hole 9'A (ie, a shaft hole), which is set correspondingly to the knife shaft mounting hole 3F on the gear bracket 3, and the said movable blade 11' is provided with '.
  • a fixed knife center hole 9'A ie, a shaft hole
  • an inner bearing 21 ′ and an outer bearing 20 are installed side by side on the gear mounting hole 3A of the gear bracket 3 without gaps.
  • the gear shaft 19 is integrally provided with a gear shaft end 19A.
  • One end of the gear shaft 19 passes through the outer bearing, the inner bearing, and the gear shaft mounting hole 3A and penetrates to the opposite side of the gear bracket 3 to be fixedly connected with the driven bevel gear 3 ′.
  • the outer side of the driven bevel gear 3 ′ is locked and fixed by a lock nut 4 ′, while the other end of the gear shaft 19 That is, the gear shaft end 19A is connected to the gear shaft connection hole 17A on the balance link bridge 17 through a connecting rod bearing 18 .
  • the swing tooth 12' meshes with the pinion shaft 19, and the power is transmitted from the pinion shaft 19 to the swing tooth 12'.
  • the movable blade 11' is fixed on the swing end of the swing tooth 12' through a fixed knife fixing bolt assembly.
  • the central hole 11'A of the movable knife on the movable blade 11' (that is, the hole of the rotating shaft) is arranged coaxially with the central hole 12'A of the swing tooth 12'.
  • the fixed blade central hole 9A on the fixed blade 9' is set corresponding to the knife shaft installation hole 3F on the gear bracket 3, and a fixed knife installation groove is arranged on the side of the gear bracket 3 towards the fixed blade.
  • a fixed knife installation protrusion matched with the fixed knife installation groove is provided on the fixed blade. The fixed knife installation protrusion is placed inside the fixed knife installation groove and limits the axial rotation of the fixed blade on the gear bracket.
  • the rotating shaft 6 (knife shaft) is set from the side where the gear bracket 3 is provided with the passive bevel gear 3' to the side of the balance link bridge 17.
  • the anti-loosening tooth piece 9 is fixedly connected with the gear bracket through the bolt 5'.
  • the fastening nut 15' and the anti-loosening screw 16' on the outside of the connecting rod bridge 17 are fixed, and the fixed blade, the moving blade, the swing tooth and the balance connecting rod bridge 17 are fixed on the gear bracket 3 in turn, and a plane needle bearing 14' is also arranged between the swing tooth and the balance connecting rod bridge 17.
  • an H-shaped "well” type parallel symmetrical stressed frame structure is formed between the gear bracket 3 and the balance link bridge 17, pinion shaft 19, and rotating shaft 6 (knife shaft), that is, a balanced stressed electric shearing tool is formed.
  • the movable blade 11' is driven by the swing tooth 12' and swings up and down with the rotating shaft 6 (cutter shaft) as the rotation center to form a shearing structure with the fixed blade 9'.
  • the movable blade 11' and the swing tooth 12' rotate coaxially.
  • the rod bearing 18 completes the connection, and the balance link bridge 17 is coaxially connected with the gear bracket 3 by the rotating shaft 6 (knife shaft).
  • the motor 100 is connected to the planetary reducer 2', the planetary reducer 2' is connected to the driving gear P and transmits the output torque to the driving gear P, and the driving gear P transmits the torque to the driven bevel gear 3'.
  • the driven bevel gear 3' is fixedly connected to the pinion shaft 19
  • the pinion shaft 19 is engaged with the driven bevel gear 3' to transmit positive and negative rotation power to the swing tooth 12', and the swing tooth 12' drives the moving blade 11' to realize opening and closing.
  • the opening and closing of the moving blades of the scissors is formed by the positive and negative rotation of the active bevel gear driven by the planetary reducer and the motor.
  • the rotating shaft 6 (knife shaft) can also pass through the connecting hole 17F of the connecting rod bridge 17 through the plane needle bearing 14', the swing tooth 12', the moving blade 11', the rotating shaft 6 (knife shaft) and the fixed blade 9', so that the swinging teeth and the moving blade can swing, pass through the gear mounting hole 3A of the gear bracket, and be fastened by a toothed nut with the same tooth shape as the anti-loosening tooth plate 9.
  • the balance link bridge 17, the gear bracket 3, the rotating shaft 6 (knife shaft) and the pinion shaft 19 form an H-shaped "well” type parallel symmetrical force-bearing frame structure.
  • the split movable blade 11' and the swing tooth 12' are installed between the gear bracket 3 and the balance link bridge 17, which completely solves the deformation of the gear bracket 3 under unilateral force when the shear exceeds the external force. At the same time, it can prevent the passive bevel gear 3' from leaving the engagement of the active bevel gear P after being stressed, and prevent the gear jumping problem of the passive bevel gear to the greatest extent.
  • Embodiment 8 is a diagrammatic representation of Embodiment 8
  • a balanced force electric shear tool its technical solution is basically the same as that of Embodiment 1, the difference is that: the end of the gear bracket 3 close to the planetary reducer is perpendicular to the axial direction of the planetary reducer.
  • the fastening holes are the fixed blade fastening upper hole 801 and the fixed blade fastening lower hole 802 .
  • two threaded holes are provided on the fixed blade 9', and the fixed blade is fastened on the gear bracket through the first fastening bolt 22' and the second fastening bolt 23 on the side of the driven bevel gear 3' from the gear bracket.
  • the central hole 9A of the fixed blade on the fixed blade 9' is a threaded hole.
  • the pendulum tooth 12' is combined with the gear shaft 19.
  • the rotating shaft 6 (cutter shaft) is directly threaded with the blade center hole 9A on the fixed blade, and then the cutter shaft passes through the cutter shaft mounting hole on the moving blade to connect with the plane needle roller bearing 14' and the balance link bridge 17.
  • an H-shaped "well” parallel symmetrical force-bearing frame structure is formed between the gear bracket 3, the balance link bridge 17, the gear shaft 19, and the rotating shaft 6 (knife shaft).
  • the movable blade and fixed blade When using the same gear bracket in this embodiment, it is only necessary to replace the movable blade and fixed blade with different tooth shafts and cutter shaft center distances and the corresponding balance connecting rod bridge, so that the torque can be increased to cut larger diameters.
  • the center distance between the gear shaft connection hole 17A and the cutter shaft connection hole 17F on the balance link bridge is increased, correspondingly replacing the elongated movable blade and the fixed blade can be used to cut branches with a larger diameter.
  • the movable blade may be a split structure of the movable blade 11' and the swing tooth 12' as shown in FIG. 11 .
  • Embodiment 9 is a diagrammatic representation of Embodiment 9:
  • a balanced force electric shearing tool has the same technical scheme as that of Embodiment 1, except that the gear bracket 3 includes a right housing with a right space 8K and a left housing with a left space 10K.
  • the shearing assembly includes a movable blade 11' and a fixed blade 9'.
  • the movable blade can be an integrated structure of the swing tooth and the blade, or can be a split structure of the blade and the swing tooth 12' as shown in FIG. 11 .
  • the active bevel gear P is supported and installed in the gear bracket 3 by the gear bearing M and the anti-retraction spring C.
  • the output end 2A of the planetary reducer is connected to the active bevel gear P, and the power meshing is transmitted to the passive bevel gear 3'.
  • the passive bevel gear 3' is fixedly connected with the pinion shaft 19 and converts the rotational engagement of the pinion shaft 19 and the movable blade 11' into shearing to complete the work.
  • the right side support bearing 4F and the left side support bearing 18A are arranged respectively on the gear shaft 19 outside the passive bevel gear 3' and the balance link bridge 17, and the right side support bearing 4F and the left side support bearing 18A are respectively arranged in the scissors casing (the scissors casing is not shown in the figure), and the connecting rod bearing 18 supporting the balance link bridge 17 is arranged side by side on the gear shaft 19 inside the left side support bearing 18A.
  • an H-type "well” type parallel symmetrical stressed frame structure is formed between the right housing with the right space 8K, the balance link bridge 17 and the left housing with the left space 10K, the pinion shaft 19, and the rotating shaft 6 (knife shaft).
  • the gear bracket 3 and the fixed blade 9' are connected in the way of bosses and through-holes, that is, the gear bracket 3 is provided with a boss 27, and the fixed blade 9' is provided with a through hole 14A.
  • the boss 27 is matched with the 14A and connected with the two threaded holes on the fixed blade 9' by the connecting bolt 30, so that the fixed blade 9' is detachably fastened on the gear bracket 3.
  • An oblate through hole is arranged inside the boss 27 .
  • Oblate through-holes include but are not limited to double oblate or hexagonal shapes, as long as they can restrict the rotating shaft 6 (knife shaft) from rotating with the center of the shaft with a very small clearance.
  • the rotating shaft 6 penetrates through the knife shaft connection hole 17F in the direction of the balance link bridge 17, passes through the oblate through hole of the plane needle bearing 14', the moving blade 11', the fixed blade 9' and the gear bracket 3, and is fastened by a nut.
  • the driven bevel gear 3' is supported on the gear bracket 3 by the gear shaft 19 and the bearing, and is fastened and compressed by the plane needle bearing, the bearing spacer, the back cover bolts and the gear bracket 3 to prevent the driven bevel gear from shaking under force.
  • a rear cover 803 is also arranged outside the driven gear 3 .
  • the structure between the gear bracket 3 and the balance link bridge 17, the pinion shaft 19, and the rotating shaft 6 (knife shaft) forms an H-shaped "well” type parallel symmetrical force-bearing frame structure.
  • An H-shaped "well” parallel symmetrical force-bearing frame structure is formed. .
  • the movable blade may be an integral structure of the swing tooth and the blade as shown in FIG. 14 , or may be a separate structure of the blade and the swing tooth 12 ′ as shown in FIG. 11 .
  • a balanced force-bearing electric shearing tool its technical solution is basically the same as that of Embodiment 1, except that the motor 100 and the planetary reducer 2 ′ are vertically installed with the gear bracket 3 and coaxially driven with the gear shaft 19 . Fasten the gear bracket 3 with the rear cover bolt 804 through a rear cover 803, and directly connect the planetary reducer 2' and the pinion shaft 19.
  • the structure between the gear bracket 3 and the balance link bridge 17, the gear shaft 19, and the rotating shaft 6 forms a balanced and symmetrical force-bearing frame structure.
  • the movable blade 11' can be an integral structure of the swing tooth and the blade as shown in FIG. 14 , or can be a separate structure of the movable blade and the swing tooth 12' as shown in FIG. 11 .
  • This embodiment can share the cutter head structure of embodiment 2 and embodiment 3.
  • the penetrating directions of the cutter shafts in the above embodiments can be used in common with each other according to the corresponding structures.
  • the driven wheel bevel tooth compression lock nut 4' or the anti-loosening tooth plate 9 or the plane needle roller bearing 14' can be canceled separately or all without use.
  • the active bevel gear P can be optionally installed with two or three gear bearings M supports.
  • the anti-bending tooth-skipping mechanism of the gears on both sides of the symmetrical force and the electric pruning shears, the gear bracket, the anti-skipping parts (i.e., the balance connecting rod bridge), the gear shaft, and the rotating shaft (cutter shaft) form a H-shaped "well" flat surface of the gears on both sides of the symmetrical force.
  • the symmetrical force-bearing frame structure, the balance link bridge prevents the gear bracket from bending and the swing tooth is installed between the gear bracket and the balance link bridge.
  • This balanced force electric shearing tool directly solves the maintenance troubles of fruit farmers, garden pruning, construction (PVC plastic) water pipe cutting, pliers operations and other related workers due to the bending of the gear bracket of the scissors and pliers opening and closing tools and the inability to work due to tooth jumping.
  • the scope of use of the tool can be changed by changing the fixed knife assembly and/or the movable knife assembly.
  • the fixed blade and the movable blade can be assembled into electric scissors.
  • Changing the shape of the fixed blade and the movable blade can change the electric scissors into an electric cutter for building and installing PVC plastic water pipes.
  • It can also be a variety of opening and closing tools for various industries that require opening and closing actions. For example, it can be replaced with tools such as pliers or animal ear marking jigs, branch grafting jigs, and other opening and closing tools.
  • orientation descriptions such as up, down, front, rear, left, right, etc. indicated orientations or positional relationships are based on the orientations or positional relationships shown in the drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the referred device or element must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as limiting the present invention.
  • the present invention is not limited to the examples described above, and changes, modifications, additions or substitutions made by those skilled in the art within the essential scope of the present invention should be regarded as the protection scope of the present invention.

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Abstract

一种齿轮副，包括相互啮合的主动齿轮（4）和被动侧摆齿轮（5），主动齿轮和被动侧摆齿轮上设置有防跳齿结构，防跳齿结构为齿面角度为75度～90度的齿面（57），在被动侧摆齿轮上该齿面为被动侧摆齿轮摆动啮合时的剪切受力工作面，剪切受力工作面与水平面之间的夹角为0～15度。还涉及一种齿轮防跳齿机构、电动剪钳式工具、伞齿轮副。该齿轮防跳齿机构减小了被动侧摆齿轮向外偏的法向力，从而使被动侧摆齿轮不易打滑跳齿，使得被动侧摆齿轮剪切受力始终朝向与主动齿轮啮合方向，即剪切力在被动侧摆齿轮与主动齿轮啮合反向的力被有效减小，脱离啮合的力被有效降低，从而降低了齿轮打滑的风险，解决了被动侧摆齿轮跳齿问题。

Description

一种齿轮副、齿轮防跳齿机构及电动剪钳式工具 技术领域
本发明属于齿轮传动技术领域，尤其是涉及一种齿轮副、齿轮防跳齿机构及电动剪、钳式工具。
背景技术
齿轮传动式开合作业工具，是人们常用的作业工具，但是由于开合式作业工具在使用过程中需要承受外力进而实现剪切等功能，因此，外力过大很容易使得齿轮在受力作用下打滑，造成跳齿，而导致工无法正常使用等问题，例如，用于林业及种植业修剪用的电动剪刀，正常情况下，在剪切较小树枝时，通过电动剪刀，可快速将多余的树枝剪除，方便省力，但是如果剪切较大树枝，则由于外力过大，会造成齿轮脱齿问题等，即现有电动剪刀在工作方式时被动侧摆锥齿轮在剪切受力时容易打滑跳齿使剪刀无法工作。而且现有的开合作业工具都是根据规格设定好，一种开合工具只能满足同一作业或同一规格的作业要求，而无法实现通过快速更换开合部件，例如剪切刀片来实现通用性设计的要求。
例如，中国专利文献(公告日：2021年4月9日，公告号：CN212910875U)公开了一种具有防跳齿功能的单动刀片电动剪刀，其包括支架、以可转动的方式安装于该支架上的摆齿和安装于摆齿上并由摆齿驱动以旋转的活动刀片、固定于支架上并与活动刀片适配的固定刀片以及用于驱动该摆齿摆动的伞齿轮及驱动装置，支架侧面螺旋安装有可调节相对位置的防跳齿螺丝，防跳齿螺丝端部显露于支架内侧面，并与摆齿外侧面之间形成有间隔。当剪切尺寸较大的树枝时，活动刀片会受到很大法向力而向外偏，以致连带该摆齿也会向外偏以发生变形，此时，该摆齿外侧面则会与防跳齿螺丝端部接触，起到支撑作用,防止摆齿在变形到超过伞齿轮啮合高度时失效,且防跳齿螺丝对摆齿形成有效的限位,保证摆齿与伞齿轮啮合，防止出现跳齿现象。
上述技术方案是通过设置防跳齿螺丝来实现防止出现跳齿现象的，但是该技术方案为这种防跳齿螺丝是点式受力防跳齿，在活动刀片受到很大的法向力向外偏时，摆齿向外偏，此时防跳齿螺丝对摆齿实现点式支撑，会导致摆齿单点受力，受力不均，仍然会存在摆齿受力产生摆动，存在跳齿及变形风险。
发明内容
本发明的第一个发明目的是为了解决现有的齿轮副在齿轮传动过程中易打滑，造成跳齿现象，以及齿轮传动式剪刀或钳类开合作业工具，在使用过程中易打滑，造成跳齿 现象，影响工具的正常使用，同时克服现有的防跳齿结构单点受力，受力不均，无法真正解决防跳齿问题，而提供一种齿轮副、一种伞齿轮副，通过啮合齿自身的齿形结构实现啮合式防跳齿、使得齿轮副在工作过程中始终能够啮合工作，而不脱齿。
本发明的第二个发明目的是提供一种齿轮防跳齿机构，通过齿轮副自身的齿形、面接触式防跳齿部件的单独或共同形成的防跳齿机构，使摆齿均匀受力，能够有效避免跳齿现象的发生。或者提供一种齿轮防跳齿机构，有效防止因齿轮支架单侧受力而产生弯曲变形现象的发生，防止剪切过程中跳齿现象的发生。
本发明的第三个发明目的是提供一种能够快速更换开合部件的电动剪、钳式工具；以及一种平衡受力电动剪切工具，以解决齿轮支架在单侧受力作用下容易产生弯曲变形，使伞齿轮副及摆齿轮副脱离齿轮接触产生跳齿等问题，
本发明实现其第一个发明目的所采用的技术方案是：一种齿轮副，包括相互啮合的主动齿轮和被动侧摆齿轮，所述的主动齿轮和被动侧摆齿轮上设置有防跳齿结构，所述的防跳齿结构为齿面角度为75度～90度的齿面，在被动侧摆齿轮上该齿面为被动侧摆齿轮摆动啮合时的剪切受力工作面，剪切受力工作面与水平面之间的夹角为0～15度。该齿轮副，通过在主动齿轮和被动齿轮上配合设置防跳齿的齿面，该齿面呈近似直角梯形结构，使被动侧摆齿轮的受力方向主要作用在该齿面上，极大的减小了被动侧摆齿轮向外偏的法向力从而使被动侧摆齿轮不易打滑跳齿，使得被动侧摆齿轮剪切受力始终朝向与主动齿轮啮合方向，即剪切力在被动侧摆齿轮与主动齿轮啮合反向的力被有效减小，也就是脱离啮合的力被有效降低，从而降低了齿轮打滑的风险，彻底解决了被动侧摆齿轮跳齿问题。
作为优选，所述的主动齿轮为主动锥齿轮，所述的主动齿轮包括弧齿锥齿轮和直齿锥齿轮；所述的被动侧摆齿轮为被动侧摆锥齿轮，所述的被动侧摆齿轮包括弧齿锥齿轮和直齿锥齿轮。
本发明实现其第二个发明目的所采用的技术方案是：一种带有齿轮副的齿轮防跳齿机构，包括齿轮支架、设置在齿轮支架上并通过齿轮副啮合式开合的定组件和动组件，在被动侧摆齿轮上形成防跳齿结构的齿面为动组件往闭口方向时的剪切受力工作面。该齿轮防跳齿机构，在齿轮副上设置有防跳齿结构，防跳齿结构使被动侧摆齿轮与主动齿轮啮合受到剪切力时，剪切力的受力方向作用在防跳齿结构上，极大的减小了被动侧摆齿轮向外偏的法向力从而使被动侧摆齿轮不易打滑跳齿，使得被动侧摆齿轮剪切受力始终朝向与主动齿轮啮合方向，即剪切力在被动侧摆齿轮与主动齿轮啮合反向的力被有效 减小，也就是脱离啮合的力被有效降低，从而降低了齿轮打滑的风险，彻底解决了被动侧摆齿轮跳齿问题。被动侧摆锥齿轮的齿形设置呈近似直角梯形结构，其近似直角的齿面设置为剪切的动组件往闭口方向时剪切受力工作面，剪切受力工作面角度接与水平面夹角为0～15度之间，使被动侧摆齿轮的受力方向主要作用在动组件上，极大的减小了被动侧摆齿轮向外偏的法向力从而使被动侧摆齿轮不易打滑跳齿；当然，剪切力小的情况下可以放宽此角度范围。主动齿轮上对应的也设置有呈近似直角梯形结构的齿面以与被动侧摆齿轮配对设置相互啮合。
作为优选，在所述的被动侧摆齿轮外侧设置有防跳齿部件，所述的防跳齿部件内侧面与被动侧摆齿轮外侧面之间设置有间隙；所述的防跳齿部件与齿轮支架形成对称式受力结构。在被动侧摆齿轮外侧安装有防跳齿部件，通过防跳齿结构和防跳齿部件实现双重防跳齿，防跳齿部件使得被动侧摆齿轮处于齿轮支架和防跳齿部件之间，齿轮支架与防跳齿部件形成两侧对称受力结构，避免了在剪切过程中齿轮支架单侧受力弯曲变形的问题，提高了剪切的稳定性；防跳齿部件内侧面与被动侧摆齿轮外侧面保持足够小的间隙，当被动侧摆齿轮受到较大的外力预产生变形时，足够小的间隙使得被动侧摆齿轮的外侧面与防跳齿部件内侧面贴合，通过面面配合阻止了被动侧摆齿轮向外侧变形跳齿现象的发生。
作为优选，所述的防跳齿部件包括一体设置的齿轮支架连接端和转轴连接端，在所述的转轴连接端设置有轴孔，所述齿轮支架连接端设置有多个固定孔；所述的防跳齿部件的转轴连接端与被动侧摆齿轮之间通过平面接触或通过一平面推力轴承接触；所述的防跳齿部件的齿轮支架连接端内侧面与被动侧摆齿轮外侧面之间设置有间隙。防跳齿部件优选对称受力防跳齿连杆，防跳齿部件上述结构既方便通过轴孔与转轴连接，实现与被动侧摆齿轮以及动组件的同轴设置，同时，在齿轮支架连接端设置多个固定孔方便通过紧固件与齿轮支架连接从而与齿轮支架形成U形对称受力结构，而且这种U形对称受力结构还方便定组件和动组件的快速更换，而不需要拆卸对称受力防跳齿连接就能够实现动组件和定组件的更换，以实现通用性结构的设计。而被动侧摆齿轮外侧面与防跳齿部件内侧面之间的间隙足够小，该间隙一般在加工时就可以设置好各零件尺寸，不同开合部件的安装尺寸相对应。
作为优选，所述的主动齿轮为主动锥齿轮，所述的主动齿轮包括弧齿锥齿轮和直齿锥齿轮。所述的主动齿轮安装在齿轮支架上并与动力机构力传递式连接，所述的动组件与被动侧摆齿轮连接并通过一转轴与齿轮支架转动连接。
作为优选，所述的被动侧摆齿轮为被动侧摆锥齿轮，所述的被动侧摆齿轮包括弧齿锥齿轮和直齿锥齿轮；所述的被动侧摆齿轮呈摆杆式结构设置有齿轮端和摆动端，所述的齿轮端与主动齿轮啮合。
作为优选，所述的定组件上设置有齿轮支架固定孔和转轴孔；所述的动组件上设置有转动轴孔和固定销孔。定组件上设置齿轮支架固定孔的设置是为了与方便定组件与齿轮支架的固定连接，而转轴孔的设置来是为了方便定组件与转轴螺纹固定连接。动组件上设置转动轴孔是为了方便与转轴的转动连接，而固定销孔是为了方便通过连接将动组件与被动侧摆齿轮连接。
作为优选，所述的齿轮支架包括一体式设置的连接体和安装体。齿轮支架的上述结构，通过连接体可以与电机及减速器壳体连接，通过安装体可以实现对主动齿轮、定组件、动组件以及防跳齿部件的安装，同时还能够使得齿轮支架与防跳齿部件组合形成对称受力结构，该对称受力结构可以有效实现被动侧摆齿轮的单侧齿轮防跳齿，而安装体可以沿连接体的轴线呈左侧式安装或右侧式安装，即防跳齿部件可以是以使用方向设置在齿轮支架的左侧或右侧。
作为优选，所述的转轴结构根据齿轮支架、定组件、动组件、被动侧摆齿轮以及防跳齿部件的同轴设置结构而设计，包括从齿轮支架侧穿入式结构和从防跳齿部件侧穿入式结构。由于被动侧摆齿轮可以设置在齿轮支架的左侧或右侧，因此防跳齿部件对应的设置在左侧和右侧，而转轴也对应的从右侧和左侧穿入实现连接。因此，转轴可以设置为不同的结构形状，具体操作根据实际需要来设置。
本发明实现其第三个发明目的所采用的技术方案是：一种电动剪钳式工具，包括电机、减速器和所述的齿轮防跳齿机构。
作为优选，所述的电机连接减速器，所述的减速器连接齿轮支架及主动齿轮并将输出扭力传递给主动齿轮，所述的主动齿轮将扭力传递给被动侧摆齿轮，被动侧摆齿轮带动定组件实现开合。
该电动剪钳式工具，包括设置在机壳里面的电机、减速器、定组件和动组件，电机连接减速器，减速器连接主动齿轮并传递输出扭力，主动齿轮将扭力传递给被动侧摆齿轮，并使被动侧摆齿轮与其连接的动组件以转轴为旋转中心进行张开闭合摆动，动组件与定组件形成剪切模式或钳式模式，所述转轴与定组件将齿轮支架紧固于中间，同时动组件、被动侧摆锥齿轮及防跳齿部件通过转轴贯穿并由紧固螺母及防松螺钉紧固，从而形成电动剪刀或电动钳等开合工具。该电动剪钳式工具，由于设置防跳齿结构或设置有 防跳齿结构和防跳齿部件这种双重防跳齿机构，彻底解决了被动侧摆齿轮跳齿问题，使其始终与主动齿轮啮合，不会出现打滑跳齿，保证正常的开合工作。
本发明实现其第一个发明目的所采用另一个优选的技术方案是：一种伞齿轮副，包括相互啮合的主动伞齿轮和被动伞齿轮，所述的主动伞齿轮和被动伞齿轮分别包括弧齿锥齿轮和直齿锥齿轮；所述的伞齿轮副的齿形呈直角梯形的直角面受力结构设置，被动轮伞齿齿形呈现接近直角梯形的齿形结构设置，接近直角梯形的齿面为剪刀闭口时的剪切受力工作面，剪切受力工作面与水平面之间的夹角为0～15度。
本发明实现其第二个发明目的所采用另一个优选的技术方案是：一种带有伞齿轮副的齿轮防跳齿机构，包括齿轮支架、设置在齿轮支架上并通过齿轮副啮合式开合的剪切组件，在所述的剪切组件外侧设置有防跳齿部件；所述的齿轮支架与防跳齿部件形成对称受力结构。
作为优选，所述的伞齿轮副通过一齿轴设置在齿轮支架上，所述的剪切组件通过一转轴设置在齿轮支架上，所述的对称式受力结构与齿轴和转轴形成对称平衡受力结构。
作为优选，所述的对称平衡受力结构呈井式结构设置；所述的齿轴和转轴构成剪切组件开合剪切力的双受力支撑梁，所述的齿轮支架和防跳齿部件构成剪切组件两侧限位平衡受力防脱齿双梁架结构。对称平衡受力结构由沿轴向设置的齿轮支架和防跳齿部件、沿垂直于齿轮支架和防跳齿部件的齿轴和转轴共同形成井式结构，齿轴和转轴构成剪切组件剪切受力的双受力支撑梁，从而形成前后支撑受力的结构，而齿轮支架和防跳齿部件构成剪切组件两侧限位平衡受力防脱齿双梁架结构，能有效防止齿轮支架的弯曲变形以及脱齿现象，而且使得两侧受力有效保证了剪切过程的平稳性。
本发明实现其第三个发明目的所采用的优选技术方案是：一种平衡受力电动剪切工具，包括所述的齿轮防跳齿机构，还包括动力组件，所述的动力组件包括电机和行星减速器。动力组件设置有电机和行星减速器，通过电机将动力传递给主动伞齿轮，主动伞齿轮将动力传递给被动伞齿轮，被动伞齿轮带动齿轴加转动，从而将动力传递给剪切组件，实现剪切。该平衡受力电动剪切工具，通过一齿轮支架和一防跳齿部件以及一齿轴和一转轴(即刀轴)共同形成一平衡受力结构，使得剪切组件在剪切过程中，剪切过程中产生的力会向齿轮支架和防跳齿部件两侧平衡传递，有效防止了因齿轮支架单侧受力而产生弯曲变形现象的发生，同时，也防止了剪切过程中跳齿现象的发生，极大的减小了剪切组件受力时，使剪切组件和齿轴往相反方向偏离导致齿轮支架弯曲变形，从而也使齿轮传动组件免于偏离啮合方向，使齿轮传动组件和剪切组件都不易打滑跳齿，即剪 切力在剪切组件与齿轮传动组件啮合反向的力被有效减小，也就是脱离啮合的力被有效降低，从而降低了齿轮打滑的风险，彻底解决了齿轮支架受力容易产生弯曲变形以及齿轮传动组件和剪切组件打滑跳齿问题。同时，由于在垂直于齿轮支架和防跳齿部件轴向设置有齿轴和转轴，在剪切受力过程中，剪切组件由前后两个支撑受力梁，使得剪切操作更加稳定，整个剪切工具前后左右平衡受力，操作更加平稳，使用寿命更长。
作为优选，所述的防跳齿部件为一平衡连杆桥，所述的平衡连杆桥的两端分别设置有齿轴连接孔和刀轴连接孔。平衡连杆桥以连杆结构作为优先方案，前后设置有齿轴连接孔和刀轴连接孔从而形成桥式受力结构，防止剪切组件因受力向外滑脱，出现脱齿现象，也避免了齿轮支架单侧受力产生弯曲变形现象的发生。
作为优选，所述的剪切组件包括动剪切组件和定剪切组件，所述的定剪切组件包括定刀固定部和定刀片，所述的定刀固定部与齿轮支架连接，所述的动剪切组件包括摆齿和动刀片，所述的摆齿与齿轴相啮合带动动刀片开合与定剪切组件形成剪切结构。作为一种优选方案，剪切组件包括动剪切组件和定剪切组件，定剪切组件包括定刀片与定刀固定部，定刀固定部是用于实现与齿轮支架的固定连接，以使定刀片相对于齿轮支架固定，而动剪切组件则包括与齿轴啮合的摆齿和动刀片，动刀片通过齿轴传递的动力由摆齿带动配合定刀片开合实现剪切功能。
作为优选，所述的摆齿和动刀片为分体式结构，所述的动刀片与摆齿通过紧固件固定连接；所述的摆齿上设置有摆齿中心孔，所述的动刀片上设置有动刀中心孔，所述的摆齿中心孔和动刀中心孔同轴设置。摆齿和动刀片设置为分体式结构，摆齿与齿轴啮合，而动刀片与摆齿固定连接，在摆齿上设置摆齿中心孔方便摆齿与动刀片共同与刀轴实现同轴连接，从而使得摆齿和动刀片以刀轴为中心进行旋转，进而与定刀片形成剪切模式，也实现了剪切组件的双梁支撑受力结构。
作为优选，所述的摆齿和动刀片为一体式结构，一体式摆齿和动刀片的中部位置设置有刀轴安装孔。作为另一种优选方案，摆齿和动刀片设置成一体式结构，摆齿端与齿轴啮合，而动刀片端与定刀片配合形成剪切结构，这样的动剪切组件更容易设置，还可以实现加长型刀片的设置，更方便对齿轴与刀轴的中心距离的变化设计，可以加长齿轴与刀轴之间的中心距离，使力矩加大即可以剪切更大直径。
作为优选，所述的齿轮支架为一体式支架结构，所述的齿轮支架上靠近动力组件的一端设置有齿轴安装孔，所述的齿轴安装孔的轴线垂直于动力组件输出轴线设置或者与动力组件输出轴线同轴设置；所述的齿轮支架上远离动力组件的一端设置有刀轴安装孔 或者设置有定刀片紧固上孔和定刀片紧固下孔。作为一种优选方案，齿轮支架设置为一体式支架结构，电机与行星减速器连接，而行星减速器与齿轮传动组件连接，齿轮传动组件与齿轴连接，因此，在齿轮支架上设置有齿轴安装孔，为了实现双梁支撑受力结构，在齿轮支架的另一端设置有刀轴安装孔，从而方便刀轴的安装，进而形成双受力支撑梁结构。作为另一种优先方案，齿轮支架的另一端设置有定刀片紧固上孔和定刀片紧固下孔，方便定剪切组件直接与齿轮支架固定连接，该方案中定剪切组件与齿轮支架作为一个整体，刀轴直接与定剪切组件连接，同样实现双受力支撑梁结构。在另一优选方案中齿轮支架上的齿轮轴安装孔与动力组件输出轴同轴线设置，也就是说行星减速器与齿轴同轴传动。
作为优选，所述的齿轮支架分体式壳体结构，包括带右空间的右外壳和带左空间的左外壳，所述的剪切组件设置在右外壳和左外壳之间。作为另一种优选方案，齿轮支架也可以是分体式壳体结构，即可以将齿轮支架与剪切工具的壳体做成一体式结构，具体的，包括左外壳和右外壳，左外壳和右外壳上分别带有左空间和右空间，用于剪切组件安装后的剪切活动空间。这样的结构同样可以与平衡连杆桥形成左右对称式结构，并与齿轴和刀轴形成井式对称平衡受力结构。
本发明的有益效果：本发明中的齿轮副、齿轮防跳齿机构，彻底解决了齿轮跳齿的问题，防跳齿结构使被动侧摆齿轮与主动齿轮啮合受到剪切力时，剪切力的受力方向作用在防跳齿结构上，极大的减小了被动侧摆齿轮向外偏的法向力从而使被动侧摆齿轮不易打滑跳齿，使得被动侧摆齿轮剪切受力始终朝向与主动齿轮啮合方向，即剪切力在被动侧摆齿轮与主动齿轮啮合反向的力被有效减小，也就是脱离啮合的力被有效降低，从而降低了齿轮打滑的风险，彻底解决了被动侧摆齿轮跳齿问题。防跳齿部件与齿轮支架形成U型对称受力结构，防止齿轮支架单边受力弯曲变形，防跳齿部件与被动侧摆齿轮外侧保持足够小的间隙使被动侧摆齿轮超过外力时可以被阻挡，被动侧摆锥齿轮受力后始终保持与主动齿轮的啮合，不会产生跳齿，实现了被动侧摆齿轮面式防跳齿结构的设计，彻底解决了被动侧摆齿轮跳齿问题；并可以直接解决果农、园林修剪、建筑水管剪切，钳类作业等相关工作者由于剪刀、钳类开合工具跳齿无法工作产生的维修烦恼。
本发明中的伞齿轮副以及平衡受力电动剪切工具，极大的减小了剪切组件受力时，使剪切组件和齿轴往相反方向偏离导致齿轮支架弯曲变形，从而也使齿轮传动组件免于偏离啮合方向，使齿轮传动组件和剪切组件都不易打滑跳齿，即剪切力在剪切组件与齿轮传动组件啮合反向的力被有效减小，也就是脱离啮合的力被有效降低，从而降低了齿 轮打滑的风险，彻底解决了齿轮支架受力容易产生弯曲变形以及齿轮传动组件和剪切组件打滑跳齿问题。在剪切受力过程中，剪切组件由前后两个支撑受力梁，使得剪切操作更加稳定，整个剪切工具前后左右平衡受力，操作更加平稳，使用寿命更长。
附图说明
图1是本发明齿轮副的一种结构示意图；
图2是本发明防跳齿结构的一种结构示意图；
图3是本发明中防跳齿结构的另一种结构示意图；
图4是本发明齿轮防跳齿机构的一种分解结构示意图；
图5是本发明实施例3中齿轮防跳齿机构的一种结构示意图；
图6是本发明中防跳齿部件的一种结构示意图；
图7是本发明中电动剪刀开合状态的一种结构示意图；
图8是本发明实施例4中电动剪刀的一种分解结构示意图；
图9是本发明实施例5中伞齿轮副中齿形的一种结构示意图；
图10是本发明实施例6中平衡受力电动剪切工具一种打开状态结构示意图；
图11是本发明实施例7中平衡受力电动剪切工具分解结构示意图；
图12本发发明实施例8中平衡受力电动剪切工具的一种结构示意图；
图13是本发明实施例9中平衡受力电动剪切工具的一种结构示意图；
图14是本发明实施例10中平衡受力电动剪切工具的一种结构示意图；
图15是本发明中齿轴和刀轴加大中心距后的平衡受力电动剪切工具的结构示意图；
图16是本发明中实施例11中平衡受力电动剪切工具的一种结构示意图；
图中：1、定组件，11、齿轮支架固定孔，12、转轴孔，2、动组件，21、转动轴孔，22、固定销孔，3、齿轮支架，31、连接体，32、安装体，343、扳机，344、弹簧，4、主动齿轮，5、被动侧摆齿轮，51、齿轮端，52、摆动端，57、齿面，6、转轴，63、操作端，K6、轴外圆，F6、转轴外螺纹，64、转动段，65、紧固段，7、防跳齿部件，71、齿轮支架连接端，72、转轴连接端，73、轴孔，75、固定孔，8、平面推力轴承，9、防松齿片，100、电机，200、减速器，β、齿面角度，α、夹角；
2＇、行星减速器，P、主动伞齿轮，3＇、被动伞齿轮，4＇、锁紧螺母，5＇、螺栓，3、齿轮支架，3A、齿轴安装孔，3F、刀轴安装孔，9＇、定刀片，9＇A、定刀中心孔，10＇、卡簧，11＇、动刀片，11＇A、动刀中心孔，12＇、摆齿，12＇A、摆齿中心孔，13＇、刀销，14＇、平面滚针轴承，15、紧固螺母，16、防松螺钉，17、平衡连杆桥，17A、齿轴连接孔，17F、刀轴连 接孔，18、连杆轴承，19、齿轴，19A、齿轴轴端，20、外侧轴承，21＇、内侧轴承，22＇、第一紧固螺栓，23、第二紧固螺栓，24、刀轴固定件，27、凸台，M、齿轮轴承，C、止退卡簧，C1、卡簧，801、定刀片紧固上孔，802、定刀片紧固下孔，803、后盖，804、后盖螺栓，8K、右空间，10K、左空间，2A、行星减速器输出端，4F、右侧支撑轴承，18A、左侧支撑轴承，14A、通孔，30、连接螺栓。
具体实施方式
下面将结合附图以及具体实施例来详细说明本发明，在此本发明的示意性实施例以及说明用来解释本发明，但并不作为对本发明的限定。
实施例1：
在图1、图2、图3所示的实施例中，一种齿轮副，包括相互啮合的主动齿轮4和被动侧摆齿轮5，所述的主动齿轮4和被动侧摆齿轮5上设置有防跳齿结构，所述的防跳齿结构为齿面角度β为75度～90度的齿面57，在被动侧摆齿轮上该齿面为被动侧摆齿轮摆动啮合时的剪切受力工作面，剪切受力工作面与水平面之间的夹角α为0～15度。所述的主动齿轮4为主动锥齿轮，所述的主动齿轮4包括弧齿锥齿轮和直齿锥齿轮；所述的被动侧摆齿轮5为被动侧摆锥齿轮，所述的被动侧摆齿轮5包括弧齿锥齿轮和直齿锥齿轮。
如图2所示，所述的被动侧摆齿轮5设置有齿面角度β为75度～90度的齿面57，该齿面57为被动侧摆齿轮摆动啮合时剪切受力面，剪切受力面工作面与水平面之间的夹角α为0～15度。被动侧摆锥齿轮的齿形设置呈近似直角梯形结构，其近似直角的齿面设置为摆动啮合时剪切受力面，剪切受力工作面角度与水平面夹角α为0～15度之间，本实施例中，齿面角度β为75度，剪切受力工作面角度α接近于水平面15度左右，极大的减小了被动侧摆齿轮5向外偏的法向力从而使被动侧摆齿轮5不易打滑跳齿；当然，剪切力F小的情况下可以放宽此角度范围。在另一实施例中，如图3所示，齿面角度β为80度，剪切受力工作面角度α接近于水平面10度。对应的主动齿轮的齿面与被动侧摆齿轮配对啮合设置。
实施例2：
在图1、图4所示的实施例中，一种齿轮防跳齿机构，适用于多种需要开合动作的各行业开合工具，包括齿轮支架3、齿轮副组件、设置在齿轮支架3上并通过齿轮副组件啮合式开合的定组件1和动组件2，所述的齿轮副组件包括主动齿轮4和与主动齿轮4啮合的被动侧摆齿轮5，所述的定组件1固定在齿轮支架3上，所述的动组件2与被动侧摆齿轮5连接并通过一转轴6与齿轮支架3转动连接，所述的齿轮副组件上设置有防跳齿结构，所述的防跳齿结构为齿面角度β为75度～90度的齿面57，在被动侧摆齿轮上该齿面为动组件往闭口 方向时剪切受力工作面，剪切受力工作面与水平面之间的夹角α为0～15度。以使被动侧摆齿轮5的受力方向主要作用在动组件上，极大的减小了被动侧摆齿轮5向外偏的法向力从而使被动侧摆齿轮5不易打滑跳齿。
如图2所示，所述的被动侧摆齿轮5设置有齿面角度β为75度～90度的齿面57，该齿面57为动组件往闭口方向时剪切受力面，剪切受力面工作面与水平面之间的夹角α为0～15度。被动侧摆锥齿轮的齿形设置呈近似直角梯形结构，其近似直角的齿面设置为剪切的动组件往闭口方向时剪切受力面，剪切受力工作面角度与水平面夹角α为0～15度之间，本实施例中，齿面角度β为75度，剪切受力工作面角度α接近于水平面15度左右，以使被动侧摆齿轮5的受力方向主要作用在动组件上，极大的减小了被动侧摆齿轮5向外偏的法向力从而使被动侧摆齿轮5不易打滑跳齿；当然，剪切力F小的情况下可以放宽此角度范围。在另一实施例中，如图3所示，齿面角度β为80度，剪切受力工作面角度α接近于水平面10度。对应的主动齿轮的齿面与被动侧摆齿轮配对啮合设置。
实施例3：
在图5所示的实施例中，一种齿轮防跳齿机构，适用于多种需要开合动作的各行业开合工具，包括齿轮支架3、齿轮副组件、设置在齿轮支架3上并通过齿轮副组件啮合式开合的定组件1和动组件2，所述的齿轮副组件包括主动齿轮4和与主动齿轮4啮合的被动侧摆齿轮5，所述的定组件1固定在齿轮支架3上，所述的动组件2与被动侧摆齿轮5连接并通过一转轴6与齿轮支架3转动连接，所述的齿轮副组件上设置有防跳齿结构，在所述的被动侧摆齿轮5外侧设置有一防跳齿部件7，所述的防跳齿部件7内侧面与被动侧摆齿轮5外侧面之间设置有间隙；所述的防跳齿部件7与齿轮支架3形成对称式受力结构。所述的防跳齿结构为齿面角度β为75度～90度的齿面57，在被动侧摆齿轮上该齿面为动组件往闭口方向时剪切受力面，剪切受力面工作面与水平面之间的夹角α为0～15度。以使被动侧摆齿轮5的受力方向主要作用在动组件上，极大的减小了被动侧摆齿轮5向外偏的法向力从而使被动侧摆齿轮5不易打滑跳齿；
如图6所示，本实施例中防跳齿部件为一对称受力防跳齿连杆，所述的防跳齿部件7包括一体设置的齿轮支架连接端71和转轴连接端72，在所述的转轴连接端72设置有轴孔73，所述齿轮支架连接端71设置有多个固定孔75。所述的防跳齿部件7的转轴连接端与被动侧摆齿轮之间通过平面接触或通过一平面推力轴承接触；本实施例中优选通过平面推力轴承8接触。所述的防跳齿部件7的齿轮支架连接端71内侧面与被动侧摆齿轮5外侧面之间设置有间隙。通过设置防跳齿部件使其与齿轮支架形成U型对称受力结构，本实施例中防跳齿部件 的齿轮支架连接端设置呈T型结构，而转轴连接端设置呈圆形，方便通过轴孔与转轴连接，实现与被动侧摆齿轮以及动组件的同轴设置，同时，在齿轮支架连接端设置多个固定孔方便通过紧固件与齿轮支架连接从而与齿轮支架形成U形对称受力结构，多个固定孔可以根据受力需要而选择连接的数量，U形对称受力结构还方便定组件和动组件的快速更换，而不需要拆卸对称受力防跳齿连接就能够实现动组件和定组件的更换，以实现通用性结构的设计。
本实施例中，所述的主动齿轮4为主动锥齿轮，所述的主动齿轮4的齿轮副包括弧齿锥齿轮和直齿锥齿轮。所述的主动齿轮4安装在齿轮支架3上并与动力机构力传递式连接。
所述的被动侧摆齿轮5为被动侧摆锥齿轮，所述的被动侧摆齿轮5的齿轮副包括弧齿锥齿轮和直齿锥齿轮。所述的被动侧摆齿轮5呈摆杆式结构设置有齿轮端51和摆动端52，所述的齿轮端51与主动齿轮4啮合。
如图2所示，所述的被动侧摆齿轮5设置有齿面角度β为75度～90度的齿面57，该齿面57为动组件往闭口方向时剪切受力面，剪切受力面工作面与水平面之间的夹角α为0～15度。被动侧摆锥齿轮的齿形设置呈近似直角梯形结构，其近似直角的齿面设置为剪切的动组件往闭口方向时剪切受力面，剪切受力工作面角度与水平面夹角α为0～15度之间，本实施例中，齿面角度β为75度，剪切受力工作面角度α接近于水平面15度左右，以使被动侧摆齿轮5的受力方向主要作用在动组件上，极大的减小了被动侧摆齿轮5向外偏的法向力从而使被动侧摆齿轮5不易打滑跳齿；当然，剪切力F小的情况下可以放宽此角度范围。在另一实施例中，如图3所示，齿面角度β为80度，剪切受力工作面角度α接近于水平面10度。对应的主动齿轮的齿面与被动侧摆齿轮配对啮合设置。
所述的定组件1上设置有齿轮支架固定孔11和转轴孔12；所述的动组件2上设置有转动轴孔21和固定销孔22。定组件上设置齿轮支架固定孔的设置是为了与方便定组件与齿轮支架的固定连接，而转轴孔的设置来是为了方便定组件与转轴螺纹固定连接。动组件上设置转动轴孔是为了方便与转轴的转动连接，而固定销孔是为了方便通过连接将动组件与被动侧摆齿轮连接。
所述的齿轮支架3包括一体式设置的连接体31和安装体32。本实施例中，齿轮支架通过连接体可以与电机及减速器壳体连接，通过安装体可以实现对主动齿轮、定组件、动组件以及防跳齿部件的安装，同时还能够使得齿轮支架与防跳齿部件组合形成对称受力结构，而安装体可以沿连接体的轴线呈左侧式安装或右侧式安装，即防跳齿部件可以是以使用方向设置在齿轮支架的左侧或右侧。
所述的转轴6的结构根据齿轮支架、定组件、动组件、被动侧摆齿轮以及防跳齿部件的 同轴设置结构而设计，包括从齿轮支架侧穿入式结构和从防跳齿部件侧穿入式结构。由于被动侧摆齿轮可以设置在齿轮支架的左侧或右侧，因此防跳齿部件对应的设置在左侧和右侧，而转轴也对应的从右侧和左侧穿入实现连接。因此，转轴可以设置为不同的结构形状，具体操作根据实际需要来设置。
本实施例中，转轴6采用从齿轮支架侧穿入式结构，转轴6从齿轮支架方向穿入，经过齿轮支架、定刀片、动刀片、被动侧摆锥齿轮、平面推力轴承及防跳齿部件穿出，再用螺母6及螺钉防松锁紧。转轴6包括操作端63、轴外圆K6、转轴外螺纹F6、转动段64和紧固段65，转轴的轴外圆K6穿过齿轮支架上的轴孔38并与其配合，转轴外螺纹F6穿过定刀片的转轴孔12并与定刀片螺纹配合，转动段64穿过动刀片、被动侧摆锥齿轮、平面推力轴承8及防跳齿部件，实现转动连接，并通过螺母及防松螺钉与紧固段64锁紧。
如图7所示，本实施例中，以该对称受力单侧齿轮防跳齿机构应用在电动剪刀为例，对称受力单侧齿轮防跳齿机构包括齿轮支架3、定刀组件1为定刀片、动刀组件2为动刀片、被动侧摆齿轮为被动侧摆锥齿轮、主动齿轮4为主动锥齿轮、转轴6为刀轴；主动锥齿轮与被动侧摆锥齿轮啮合，被动侧摆锥齿轮与动刀片通过一刀销连接，被动侧摆锥齿轮带动动刀片以刀轴为旋转中心使其张开闭合摆动与定刀片形成剪切模式。刀轴与定刀片的内螺纹将齿轮支架紧固于中间，同时动刀片、被动侧摆锥齿轮、平面推力轴承及防跳齿部件通过刀轴贯穿由紧固螺母及防松螺钉紧固。
本实施例中，所述被动侧摆锥齿轮安装在齿轮支架和防跳齿部件之间，被动侧摆锥齿轮外侧面设有连接齿轮支架与刀轴的防跳齿部件7，防跳齿部件作用是防止齿轮支架单边受力弯曲变形，防跳齿部件内侧面与被动侧摆锥齿轮外侧面保持足够小的间隙约0.2mm左右，形成对被动侧持锥齿轮的面式防跳齿结构，使被动侧摆锥齿轮超过外力时可以阻挡被动侧摆锥齿轮受力后离开主动锥齿轮的啮合，彻底解决被动侧摆锥齿轮跳齿问题。
本实施例中，防跳齿部件7的齿轮支架连接端71通过设置在固定孔75内的螺栓及螺母紧固在齿轮支架3上，螺栓的设置数量根据剪切力的大小设置，例如，剪切较小直径树枝等物体，也可以减少螺母及螺栓的数量；其转轴连接端72通过轴孔73与刀轴连接，并由螺母及防松螺钉紧固；在被动侧摆锥齿轮与防跳齿部件之间平面连接或者通过设置一平面推力轴承8实现连接，本实施例中通过平面推力轴承8实现连接。在另一实施例中，也可以不使用平面推力轴承，直接采用被动侧摆锥齿轮与防跳齿部件平面接触。
为了方便操作，在另一实施例中还设置有扳机343和弹簧344，所述扳机、弹簧可以设置在齿轮支架上，也可以设置在外壳上。
所述被动侧摆齿轮及定组件、动组件可以设置成在剪刀的左边或右边都可以安装使用。
本实施例中，一种电动剪刀，包括电机100、减速器200和上述实施例所述的齿轮防跳齿机构。所述的电机100连接减速器200，所述的减速器200连接齿轮支架3及主动齿轮并将输出扭力传递给主动齿轮，所述的主动齿轮将扭力传递给被动侧摆齿轮，被动侧摆齿轮带动定组件实现开合。所述剪刀动刀的开合由减速器和电机带动主动锥齿轮正反旋转形成。
实施例4：
在图8所示的实施例中，其技术方案与实施例4基本相同，不同之处在于：转轴与定组件即定刀片通过螺纹配合，定刀片的内螺纹与转轴的外螺纹配合，转轴的端部由防松齿片和螺丝紧固。
上述实施例所述的防跳齿机构，在齿轮副组件上设置有防跳齿结构，防跳齿结构使被动侧摆齿轮与主动齿轮啮合受到剪切力时，剪切力的受力方向作用在防跳齿结构上，极大的减小了被动侧摆齿轮向外偏的法向力从而使被动侧摆齿轮不易打滑跳齿，使得被动侧摆齿轮剪切受力始终朝向与主动齿轮啮合方向，即剪切力在被动侧摆齿轮与主动齿轮啮合反向的力被有效减小，也就是脱离啮合的力被有效降低，从而降低了齿轮打滑的风险，彻底解决了被动侧摆齿轮跳齿问题。或在齿轮副组件上设置有防跳齿结构同时在被动侧摆齿轮外侧安装有防跳齿部件，通过防跳齿结构和防跳齿部件实现双重防跳齿，防跳齿结构以使被动侧摆齿轮的受力方向主要作用在动组件上，极大的减小了被动侧摆齿轮向外偏的法向力从而使被动侧摆齿轮不易打滑跳齿，在被动侧摆齿轮外侧安装防跳齿部件，使得被动侧摆齿轮处于齿轮支架和防跳齿部件之间，呈三明治结构设置，齿轮支架与防跳齿部件形成两侧对称受力结构，避免了在剪切或钳夹过程中齿轮支架单侧受力的问题，避免了齿轮支架单边受力弯曲变形的问题，提高了剪切或钳夹的稳定性；而被动侧摆齿轮外侧面与防跳齿部件内侧面之间设置有间隙，防跳齿部件内侧面与被动侧摆齿轮外侧面保持足够小的间隙，既不会影响被动侧摆齿轮带动动组件的开合，还能够彻底解决被动侧摆齿轮跳齿问题，防跳齿部件能够对被动侧摆齿轮在剪切受力时进行阻挡，使其始终与主动齿轮啮合，不会出现打滑跳齿，保证正常的开合工作。
该电动剪钳式工具，直接解决了果农、园林修剪、建筑(PVC塑胶)水管剪切，钳类作业等相关工作者由于剪刀、钳类开合工具跳齿无法工作产生的维修烦恼。通过更换定组件和或动组件来改变工具的使用范围，例如设置为定刀片、动刀片可以组装成电动剪刀，改变定刀片可以使电动剪刀改变为应用于建筑安装PVC塑胶水管的电动裁切刀，还可以是其他多种需要开合动作的各行业用开合工具。例如换成钳体一类的或者动物耳朵打标夹具、树枝嫁接 夹具等等开合动作的工具。
实施例5：
在图9所示的实施例中，一种伞齿轮副，包括相互啮合的主动伞齿轮P和被动伞齿轮3＇，所述的主动伞齿轮P和被动伞齿轮3＇分别包括弧齿锥齿轮和直齿锥齿轮；所述的伞齿轮副的齿形呈直角梯形的直角面受力结构设置，被动轮伞齿齿形呈现接近直角梯形的齿形结构设置，接近直角梯形的齿面为剪刀闭口时的剪切受力工作面，剪切受力工作面与水平面之间的夹角为0～15度。优选伞齿轮副齿形呈直角梯形的直角面受力，被动轮伞齿齿形呈现近似接近直角梯形的齿形，近似直角的齿面为剪刀闭口时的剪切受力面，剪切受力工作面角度接近于水平面10度左右(0～15度之间)，例如可以是5度、10度、15度等，图9中示出的是10度和15度两种情形的齿形，主动轮齿形与被动轮摆齿配对啮合以防止伞齿受力跳齿打滑。
实施例6：
在图10所示的实施例中，一种带有伞齿轮副的齿轮防跳齿机构，包括齿轮支架3、设置在齿轮支架3上并通过齿轮副啮合式开合的剪切组件，在所述的剪切组件外侧设置有防跳齿部件7；所述的齿轮支架3与防跳齿部件7形成对称式受力结构。防跳齿部件7为一平衡连杆桥17。所述的伞齿轮副通过一齿轴19设置在齿轮支架3上，所述的剪切组件通过一转轴6(即刀轴)设置在齿轮支架3上，所述的对称式受力结构与齿轴19和转轴6(刀轴)形成对称平衡受力结构；所述的对称平衡受力结构呈井式结构设置；所述的齿轴19和转轴6(刀轴)构成剪切组件开合剪切力的双受力支撑梁，所述的齿轮支架3和防跳齿部件7构成剪切组件两侧限位平衡受力防脱齿双梁架结构。
实施例7：
在图10、图11所示的实施例中，一种平衡受力电动剪切工具，包括动力组件、齿轮传动组件和剪切组件，动力组件包括电机100和行星减速器2＇，所述的电机100连接行星减速器2＇，所述的齿轮传动组件包括主动伞齿轮P和被动伞齿轮3＇，所述的剪切组件包括动刀组件和定刀组件，所述的定刀组件包括定刀固定部和定刀片9＇，所述的定刀固定部与齿轮支架3连接，所述的动刀组件包括摆齿12＇和动刀片11＇，所述的摆齿与齿轴相啮合带动动刀片开合与定刀组件形成剪切结构。还包括一齿轮支架3和防跳齿部件7，本实施例中，防跳齿部件7为一平衡连杆桥17。本实施例中，动刀片11＇和摆齿12＇采用分体式结构设置并通过一刀销13＇、卡簧10＇进行固定连接。当然，动刀片11＇和摆齿12＇也可以采用一体式设计结构。在齿轮支架3上或者在剪切工具的外壳上还设置有扳机弹簧344和扳机343，用于实现剪切工具的操作。
所述的行星减速器2＇连接主动伞齿轮P，所述的主动伞齿轮P由齿轮轴承M、止退卡簧C、卡簧C1支撑安装在齿轮支架3内，所述的被动伞齿轮3＇与齿轴19固连并与主动伞齿轮P相啮合，主动伞齿轮P将动力啮合传递给被动伞齿轮3＇。所述的止退卡簧C对齿轮轴承M轴向限制。所述的齿轴19穿设在齿轮支架3上，所述的齿轴19与摆齿12＇相啮合并且将动力传递给摆齿12＇。摆齿12＇包括齿端和摆动端，在摆齿的摆动端设置有摆齿中心孔12＇A。
所述的齿轮支架3靠近行星减速器一端垂直于行星减速器轴向设置有齿轴安装孔3A，齿轮支架3远离行星减速器一端设置有刀轴安装孔3F，刀轴安装孔3F与齿轴安装孔3A的轴线相互平行。
所述的平衡连杆桥17的两端分别设置有齿轴连接孔17A和刀轴连接孔17F。如图15所示，平衡连杆桥17上的齿轴连接孔17A和刀轴连接孔17F孔中心距离可以根据需要进行增加，同时，对应更换加长型的动刀片和定刀片，即可形成用于更大直径的树枝的剪切工具，此时，齿轮支架、转轴6和齿轴19及平衡连杆桥之间形成的“井”式结构对应变化为加长型。在另一实施例中，加长型的动刀片即可以是一体式结构设置，也可以是如图11所述的动刀片11＇和摆齿12＇分体式结构。
定刀片9＇上设置有定刀中心孔9＇A(即转轴孔)，定刀中心孔9＇A与齿轮支架3上的刀轴安装孔3F对应设置，所述的动刀片11＇上设置有＇。
具体的，如图11所示，在齿轮支架3的齿轴安装孔3A上紧贴端面并列无隙安装有内侧轴承21＇和外侧轴承20，齿轴19上一体设置有齿轴轴端19A，齿轴19的一端穿过外侧轴承和内侧轴承以及齿轴安装孔3A并穿到齿轮支架3的对侧与被动伞齿轮3＇固定连接，被动伞齿轮3＇的外侧通过一锁紧螺母4＇锁紧固定，而齿轴19的另一端，即齿轴轴端19A通过一连杆轴承18与平衡连杆桥17上的齿轴连接孔17A连接。摆齿12＇与齿轴19互相啮合，由齿轴19将动力传递给摆齿12＇，所述的动刀片11＇通过定刀固定螺栓组件固定在摆齿12＇的摆动端。动刀片11＇上的动刀中心孔11＇A(即转动轴孔)与摆齿12＇上的摆齿中心孔12＇A同轴设置。
所述的定刀片9＇上的定刀片中心孔9A与齿轮支架3上的刀轴安装孔3F对应设置，并且在齿轮支架3的刀轴安装孔3F朝向定刀片一侧设置有定刀安装槽，所述的定刀片上设置有与定刀安装槽相配合的定刀安装凸起，定刀安装凸起卡放在定刀安装槽内部并且限位定刀片在齿轮支架上的轴向转动。
所述的转轴6(刀轴)自齿轮支架3设有被动伞齿轮3＇的一侧向平衡连杆桥17一侧设 置，在转轴(刀轴)与齿轮支架之间设置有一防松齿片9，防松齿片9通过螺栓5＇与齿轮支架固定连接，转轴6(刀轴)穿过防松齿片9、齿轮支架3上的刀轴安装孔3F、定刀上的定刀片中心孔9A、动刀片上动刀中心孔11＇A、摆齿12＇上的摆齿中心孔12＇A以及平衡连杆桥17上刀轴连接孔17F，并通过设置在平衡连杆桥17外侧的紧固螺母15＇和防松螺钉16＇固定，依次将定刀片、动刀片、摆齿和平衡连杆桥17固定在齿轮支架3上，在摆齿和平衡连杆桥17之间还设置有平面滚针轴承14＇。
此时，所述的齿轮支架3与平衡连杆桥17、齿轴19、转轴6(刀轴)之间形成H型的“井”式平行对称受力框架结构，即形成一平衡受力电动剪切工具。
该平衡受力电动剪切工具，所述的动刀片11＇在摆齿12＇带动下以转轴6(刀轴)为旋转中心上下摆动与定刀片9＇形成剪切式结构，所述的动刀片11＇与摆齿12＇同轴转动，所述的齿轴19和齿轴轴端19A为同一整体，所述的摆齿12＇外侧面和齿轴轴端19A上设置有平衡连杆桥17，齿轴19与平衡连杆桥17由连杆轴承18完成连接，平衡连杆桥17与齿轮支架3由转轴6(刀轴)同轴连接。
如图10、图11所示，所述的电机100连接行星减速器2＇，所述的行星减速器2＇连接主动齿轮P并将输出扭力传递给主动齿轮P，所述的主动齿轮P将扭力传递给被动伞齿轮3＇，由于被动伞齿轮3＇固连齿轴19，因此，齿轴19随被动伞齿轮3＇将正反旋转动力啮合传动给摆齿12＇，摆齿12＇带着动刀片11＇实现开合。所述剪刀动刀片的开合由行星减速器和电机带动主动伞齿轮正反旋转形成。
在另外的实施例中，所述转轴6(刀轴)也可以由平衡连杆桥17方向的刀轴连接孔17F穿入经由平面滚针轴承14＇、摆齿12＇、动刀片11＇、转轴6(刀轴)与定刀片9＇螺纹连接压紧，使摆齿和动刀片可以摆动，穿过齿轮支架的齿轴安装孔3A穿出，由与防松齿片9相同齿形的带齿螺母紧固。
所述的平衡连杆桥17、齿轮支架3与转轴6(刀轴)、齿轴19形成H型的“井”式平行对称受力框架结构。分体式动刀片11＇和摆齿12＇安装在齿轮支架3和平衡连杆桥17之间，彻底解决剪切超过外力时齿轮支架3单边受力弯曲变形，同时可以阻挡被动伞齿轮3＇受力后离开主动锥齿轮P的啮合，最大限度防止被动伞齿轮跳齿问题。
实施例8：
在图12所示实施例中，一种平衡受力电动剪切工具，其技术方案与实施例1基本相同，不同之处在于：所述的齿轮支架3靠近行星减速器一端垂直于行星减速器轴向设置有齿轴安装孔3A，齿轮支架3远离行星减速器一端不设置刀轴安装孔3F，而是直接在其端部设置两 紧固孔，即定刀片紧固上孔801和定刀片紧固下孔802。对应的在所述的定刀片9＇上设置有两螺纹孔，定刀片通过从齿轮支架设有被动伞齿轮3＇一侧的第一紧固螺栓22＇和第二紧固螺栓23紧固在齿轮支架上，所述的定刀片9＇上的定刀片中心孔9A为一螺纹孔，动刀片11＇和摆齿12＇采用一体式设计结构，即采用带摆齿12＇的一体式动刀片11＇，在动刀片和摆齿中间位置设置有刀轴安装孔。摆齿12＇与齿轴19哈合，本实施例中，转轴6(刀轴)直接与定刀片上的刀片中心孔9A螺纹连接，然后刀轴穿过动刀片上的刀轴安装孔与平面滚针轴承14＇、平衡连杆桥17连接。
此时，所述的齿轮支架3与平衡连杆桥17、齿轴19、转轴6(刀轴)之间形成H型的“井”式平行对称受力框架结构。
该实施例中的同一个齿轮支架时，只须更换不同齿轴和刀轴中心距的可换动刀片和定刀片及对应平衡连杆桥，使力矩加大即可以剪切更大直径。如图15所示，平衡连杆桥上齿轴连接孔17A和刀轴连接孔17F孔中心距离增加，对应更换加长型的动刀片和定刀片即可形成用于更大直径的树枝的剪切，此时，齿轮支架、转轴6(刀轴)和齿轴19及平衡连杆桥之间形成的“井”式结构对应变化为加长型。在其他实施例中，动刀片可以是如图11所述的动刀片11＇和摆齿12＇分体式结构。
实施例9：
在图13所示实施例中，一种平衡受力电动剪切工具，其技术方案与实施例1基本相同，不同之处在于：齿轮支架3包括带右空间8K的右外壳和带左空间10K的左外壳，剪切组件设置在右空间和左空间之间，所述的右外壳安装在防松齿片9内侧、转轴6(刀轴)大端内侧与定刀片9＇之间，所述的左外壳安装在紧固螺母15＇与对称受力防跳齿平衡连杆桥17之间。所述的剪切组件包括动刀片11＇和定刀片9＇。动刀片可以是摆齿与刀片一体式结构，也可以是图11所示的刀片和摆齿12＇分体式结构。
所述的主动伞齿轮P由齿轮轴承M、止退卡簧C支撑安装在齿轮支架3内，行星减速器输出端2A连接主动伞齿轮P，并将动力啮合传递给被动伞齿轮3＇，被动伞齿轮3＇与齿轴19固连并将齿轴19与动刀片11＇的旋转啮合转化为剪切完成工作。在被动伞齿轮3＇和平衡连杆桥17外侧的齿轴19上分别设置有右侧支撑轴承4F和左侧支撑轴承18A，右侧支撑轴承4F和左侧支撑轴承18A分别设置在剪刀外壳内(图中未画出剪刀外壳)，在左侧支撑轴承18A内侧的齿轴19上并排设置有支撑平衡连杆桥17的连杆轴承18。
由此，所述的带右空间8K的右外壳与平衡连杆桥17及带左空间10K的左外壳、齿轴19、转轴6(刀轴)之间形成H型的“井”式平行对称受力框架结构。
实施例10：
在图14所示实施例中，一种平衡受力电动剪切工具，其技术方案与实施例1基本相同，不同之处在于：
齿轮支架3和定刀片9＇连接方式为凸台和通孔配合式连接，即在齿轮支架3上的设置有凸台27，在定刀片9＇上设置有通孔14A，通过14A与凸台27相配合并由连接螺栓30与定刀片9＇上的两个螺纹孔固连，将定刀片9＇可拆卸地紧固在齿轮支架3上。凸台27内部设置有扁圆通孔。扁圆通孔包括并不限于双扁圆或者六方等形状，只须以极小间隙配合能限制转轴6(刀轴)以轴中心旋转就可以。
转轴6(刀轴)由平衡连杆桥17方向的刀轴连接孔17F穿入经由平面滚针轴承14＇、动刀片11＇、定刀片9＇和齿轮支架3的扁圆通孔穿出，由螺母紧固。
被动伞齿轮3＇由齿轴19和轴承支撑在齿轮支架3上，并由平面滚针轴承、轴承垫片、后盖用螺栓与齿轮支架3紧固压紧防止被动伞齿轮受力晃动。在被动齿轮3外部还设置有后盖803。
由此，所述的齿轮支架3与平衡连杆桥17、齿轴19、转轴6(刀轴)之间该结构形成H型的“井”式平行对称受力框架结构。形成H型的“井”式平行对称受力框架结构。。
本实施例中，动刀片可以是如图14所示的摆齿与刀片一体式结构，也可以是如图11所示的刀片和摆齿12＇分体式结构。
实施例11：
在图16所示实施例中，一种平衡受力电动剪切工具，其技术方案与实施例1基本相同，不同之处在于：电机100和行星减速器2＇与齿轮支架3垂直安装，并与齿轴19同轴传动。通过一后盖803用后盖螺栓804与齿轮支架3紧固，将行星减速器2＇和齿轴19直连。
由此，所述的齿轮支架3与平衡连杆桥17、齿轴19、转轴6(刀轴)之间该结构形成平衡对称受力框架结构。
本实施例中，动刀片11＇可以是如图14所示的摆齿与刀片一体式结构，也可以是如图11所示的动刀片和摆齿12＇分体式结构。此实施例可以共用实施例2、实施例3的刀头结构。
以上实施例的刀轴穿入方向根据相应结构可以互为通用。被动轮伞齿压紧锁紧螺母4＇或防松齿片9或平面滚针轴承14＇可以单独或者都取消不用。主动伞齿轮P可以选择安装两个或三个齿轮轴承M支撑。
上述实施例所述的对称受力两侧齿轮防支架弯曲跳齿机构及电动修枝剪，齿轮支架、防跳齿部件(即平衡连杆桥)、齿轴、转轴(刀轴)形成对称受力两侧齿轮H型的“井”式平 行对称受力框架结构，平衡连杆桥防齿轮支架弯曲及跳齿的摆齿安装在齿轮支架和平衡连杆桥之间，摆齿外侧有连接齿轴与转轴(刀轴)的平衡连杆桥，平衡连杆桥作用是防止齿轮支架单侧受力弯曲变形和极大减少伞齿及摆齿跳齿问题，保证正常的开合工作。
该平衡受力电动剪切工具，直接解决了果农、园林修剪、建筑(PVC塑胶)水管剪切，钳类作业等相关工作者由于剪刀、钳类开合工具齿轮支架弯曲及跳齿无法工作产生的维修烦恼。通过更换定刀组件和或动刀组件来改变工具的使用范围，例如设置为定刀片、动刀片可以组装成电动剪刀，改变定刀片和动刀片形状可以使电动剪刀改变为应用于建筑安装PVC塑胶水管的电动裁切刀，还可以是其他多种需要开合动作的各行业用开合工具。例如换成钳体一类的或者动物耳朵打标夹具、树枝嫁接夹具等等开合动作的工具。
在本发明的描述中，需要理解的是，涉及到方位描述，例如上、下、前、后、左、右等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本发明和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本发明的限制。本发明也不仅限于上述说明的举例，本技术领域的普通技术人员在本发明的实质范围内所做出的变化、改型、增添或替换，都应视为本发明的保护范围。

Claims (15)

  1. 一种齿轮副，包括相互啮合的主动齿轮(4)和被动侧摆齿轮(5)，其特征在于：所述的主动齿轮(4)和被动侧摆齿轮(5)上设置有防跳齿结构，所述的防跳齿结构为齿面角度(β)为75度～90度的齿面(57)，在被动侧摆齿轮上该齿面为被动侧摆齿轮摆动啮合时的剪切受力工作面，剪切受力工作面与水平面之间的夹角(α)为0～15度。
  2. 根据权利要求1所述的一种齿轮副，其特征在于：所述的主动齿轮(4)为主动锥齿轮，所述的主动齿轮(4)包括弧齿锥齿轮和直齿锥齿轮；所述的被动侧摆齿轮(5)为被动侧摆锥齿轮，所述的被动侧摆齿轮(5)包括弧齿锥齿轮和直齿锥齿轮。
  3. 一种带有权利要求1所述的齿轮副的齿轮防跳齿机构，其特征在于：包括齿轮支架(3)、设置在齿轮支架(3)上并通过齿轮副啮合式开合的定组件(1)和动组件(2)，在被动侧摆齿轮上形成防跳齿结构的齿面为动组件往闭口方向时的剪切受力工作面；在所述的被动侧摆齿轮(5)外侧设置有防跳齿部件(7)，所述的防跳齿部件(7)与齿轮支架(3)形成对称式受力结构。
  4. 根据权利要求3所述的齿轮防跳齿机构，其特征在于：所述的防跳齿部件(7)包括一体设置的齿轮支架连接端(71)和转轴连接端(72)，在所述的转轴连接端(72)设置有轴孔(73)，所述齿轮支架连接端(71)设置有多个固定孔(75)；所述的防跳齿部件(7)的转轴连接端与被动侧摆齿轮之间通过平面接触或通过一平面推力轴承(8)接触；所述的防跳齿部件(7)的齿轮支架连接端(71)内侧面与被动侧摆齿轮(5)外侧面之间设置有间隙。
  5. 根据权利要求3所述的齿轮防跳齿机构，其特征在于：所述的主动齿轮(4)为主动锥齿轮，所述的主动齿轮(4)包括弧齿锥齿轮和直齿锥齿轮；所述的主动齿轮(4)安装在齿轮支架(3)上并与动力机构力传递式连接，所述的动组件(2)与被动侧摆齿轮(5)连接并通过一转轴(6)与齿轮支架(3)转动连接；所述的被动侧摆齿轮(5)为被动侧摆锥齿轮，所述的被动侧摆齿轮(5)包括弧齿锥齿轮和直齿锥齿轮；所述的被动侧摆齿轮(5)呈摆杆式结构设置有齿轮端(51)和摆动端(52)，所述的齿轮端(51)与主动齿轮(4)啮合。
  6. 根据权利要求3至5任意一项所述的齿轮防跳齿机构，其特征在于：所述的定组件(1)上设置有齿轮支架固定孔(11)和转轴孔(12)；所述的动组件(2)上设置有转动轴孔(21)和固定销孔(22)。
  7. 一种电动剪钳式工具，其特征在于：包括电机(100)、减速器(200)和权利要求3至6任意一项所述的齿轮防跳齿机构；所述的电机(100)连接减速器(200)，所述的减速器(200)连接齿轮支架(3)及主动齿轮(4)并将输出扭力传递给主动齿轮(4)，所述的主动齿轮(4)将扭力传递给被动侧摆齿轮(5)，被动侧摆齿轮(5)带动定组件实现开合。
  8. 一种伞齿轮副，包括相互啮合的主动伞齿轮(P)和被动伞齿轮(3＇)，其特征在于：所述的主动伞齿轮(P)和被动伞齿轮(3＇)分别包括弧齿锥齿轮和直齿锥齿轮；所述的伞齿轮副的齿形呈直角梯形的直角面受力结构设置，被动轮伞齿齿形呈现接近直角梯形的齿形结构设置，接近直角梯形的齿面为剪刀闭口时的剪切受力工作面，剪切受力工作面与水平面之间的夹角(α)为0～15度。
  9. 一种带有权利要求8所述的伞齿轮副的齿轮防跳齿机构，包括齿轮支架(3)、设置在齿轮支架(3)上并通过齿轮副啮合式开合的剪切组件，在所述的剪切组件外侧设置有防跳齿部件(7)；所述的齿轮支架(3)与防跳齿部件(7)形成对称式受力结构。
  10. 根据权利要求9所述的齿轮防跳齿机构，其特征在于：所述的伞齿轮副通过一齿轴(19)设置在齿轮支架(3)上，所述的剪切组件通过一转轴(6)设置在齿轮支架(3)上，所述的对称式受力结构与齿轴(19)和转轴(6)形成对称平衡受力结构；所述的对称平衡受力结构呈井式结构设置；所述的齿轴(19)和转轴(6)构成剪切组件开合剪切力的双受力支撑梁，所述的齿轮支架(3)和防跳齿部件(7)构成剪切组件两侧限位平衡受力防脱齿双梁架结构。
  11. 一种平衡受力电动剪切工具，其特征在于：包括由权利要求9或10所述的齿轮防跳齿机构，还包括动力组件，所述的动力组件包括电机(1)和行星减速器(2)。
  12. 根据权利要求11所述的平衡受力电动剪切工具，其特征在于：所述的防跳齿部件(7)为一平衡连杆桥(17)，所述的平衡连杆桥(17)的两端分别设置有齿轴连接孔(17A)和刀轴连接孔(17F)。
  13. 根据权利要求11或12所述的平衡受力电动剪切工具，其特征在于：所述的剪切组件包括动刀组件和定刀组件，所述的定刀组件包括定刀固定部和定刀片(9)，所述的定刀固定部与齿轮支架(3)连接，所述的动刀组件包括摆齿(12)和动刀片(11)，所述的摆齿(12)与齿轴(19)相啮合带动动刀片(11)开合与定刀组件形成剪切结构。
  14. 根据权利要求13所述的平衡受力电动剪切工具，其特征在于：所述的摆齿(12)和动刀片(11)为分体式结构，所述的动刀片(11)与摆齿(12)通过紧固件固定连接；所述的摆齿(12)上设置有摆齿中心孔(12A)，所述的动刀片上设置有动刀中心孔(11A)，所述的摆齿中心孔(12A)和动刀中心孔(11A)同轴设置；所述的摆齿(12)和动刀片(11)为一体式结构，一体式摆齿和动刀片的中部位置设置有刀轴安装孔。
  15. 根据权利要求11或12所述的平衡受力电动剪切工具，其特征在于：所述的齿轮支架(3)为一体式支架结构，所述的齿轮支架(3)上靠近动力组件的一端设置有齿轴安装孔(3A)，所述的齿轴安装孔(3A)的轴线垂直于动力组件输出轴线设置或者与动力组件输出轴线同轴 设置；所述的齿轮支架(3)上远离动力组件的一端设置有刀轴安装孔(3F)或者设置有定刀片紧固上孔(801)和定刀片紧固下孔(802)；所述的齿轮支架(3)分体式壳体结构，包括带右空间(3K)的右外壳和带左空间(10K)的左外壳，所述的剪切组件设置在右外壳和左外壳之间。
PCT/CN2023/072070 2022-01-19 2023-01-13 一种齿轮副、齿轮防跳齿机构及电动剪钳式工具 WO2023138500A1 (zh)

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CN102099598A (zh) * 2008-07-18 2011-06-15 株式会社丰田中央研究所 准双曲面齿轮设计方法及准双曲面齿轮
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