WO2018219184A1 - 电动工具 - Google Patents

电动工具 Download PDF

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Publication number
WO2018219184A1
WO2018219184A1 PCT/CN2018/087955 CN2018087955W WO2018219184A1 WO 2018219184 A1 WO2018219184 A1 WO 2018219184A1 CN 2018087955 W CN2018087955 W CN 2018087955W WO 2018219184 A1 WO2018219184 A1 WO 2018219184A1
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WO
WIPO (PCT)
Prior art keywords
rotating wheel
power tool
weight member
plane
projection
Prior art date
Application number
PCT/CN2018/087955
Other languages
English (en)
French (fr)
Inventor
王佳
Original Assignee
博世电动工具（中国）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
Application filed by 博世电动工具（中国）有限公司 filed Critical 博世电动工具（中国）有限公司
Priority to US16/613,763 priority Critical patent/US10960474B2/en
Priority to EP18810687.6A priority patent/EP3632601A4/en
Publication of WO2018219184A1 publication Critical patent/WO2018219184A1/zh

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23D—PLANING; SLOTTING; SHEARING; BROACHING; SAWING; FILING; SCRAPING; LIKE OPERATIONS FOR WORKING METAL BY REMOVING MATERIAL, NOT OTHERWISE PROVIDED FOR
    • B23D49/00—Machines or devices for sawing with straight reciprocating saw blades, e.g. hacksaws
    • B23D49/10—Hand-held or hand-operated sawing devices with straight saw blades
    • B23D49/14—Pad saws
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23D—PLANING; SLOTTING; SHEARING; BROACHING; SAWING; FILING; SCRAPING; LIKE OPERATIONS FOR WORKING METAL BY REMOVING MATERIAL, NOT OTHERWISE PROVIDED FOR
    • B23D49/00—Machines or devices for sawing with straight reciprocating saw blades, e.g. hacksaws
    • B23D49/10—Hand-held or hand-operated sawing devices with straight saw blades
    • B23D49/16—Hand-held or hand-operated sawing devices with straight saw blades actuated by electric or magnetic power or prime movers
    • B23D49/162—Pad sawing devices
    • B23D49/165—Pad sawing devices with means to move the saw blades in an orbital path
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23D—PLANING; SLOTTING; SHEARING; BROACHING; SAWING; FILING; SCRAPING; LIKE OPERATIONS FOR WORKING METAL BY REMOVING MATERIAL, NOT OTHERWISE PROVIDED FOR
    • B23D51/00—Sawing machines or sawing devices working with straight blades, characterised only by constructional features of particular parts; Carrying or attaching means for tools, covered by this subclass, which are connected to a carrier at both ends
    • B23D51/16—Sawing machines or sawing devices working with straight blades, characterised only by constructional features of particular parts; Carrying or attaching means for tools, covered by this subclass, which are connected to a carrier at both ends of drives or feed mechanisms for straight tools, e.g. saw blades, or bows
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23D—PLANING; SLOTTING; SHEARING; BROACHING; SAWING; FILING; SCRAPING; LIKE OPERATIONS FOR WORKING METAL BY REMOVING MATERIAL, NOT OTHERWISE PROVIDED FOR
    • B23D49/00—Machines or devices for sawing with straight reciprocating saw blades, e.g. hacksaws
    • B23D49/10—Hand-held or hand-operated sawing devices with straight saw blades
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/06—Means for driving the impulse member
    • B25D11/12—Means for driving the impulse member comprising a crank mechanism
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/24—Damping the reaction force
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2217/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D2217/0073—Arrangements for damping of the reaction force
    • B25D2217/0076—Arrangements for damping of the reaction force by use of counterweights
    • B25D2217/0088—Arrangements for damping of the reaction force by use of counterweights being mechanically-driven

Definitions

  • the present application relates to the field of power tools, and more particularly to power tools that output reciprocating linear motion.
  • Common electric tools such as reciprocating saws, electric hammers, and the like, include a drive device that outputs a rotational motion, an action device that outputs a reciprocating linear motion, and a motion conversion mechanism that converts the rotational motion of the drive device into a reciprocating linear motion of the motion device.
  • the action device of this type of electric power tool performs a reciprocating impact or a reciprocating cutting operation on a target workpiece by performing a reciprocating linear motion.
  • the movement direction is frequently changed.
  • the action device that frequently changes the movement direction causes the power tool to vibrate due to inertia, thereby reducing the service life of the power tool; Physical fatigue damage also affects the operator's comfort in operating the power tool.
  • a reciprocating saw in the prior art.
  • it includes an eccentric mass similar to that described above for balancing the inertial force generated by the action device of the power tool in the direction of motion, eliminating the resulting inertial force. Vibration.
  • this eccentric mass generates a force component in a horizontal direction perpendicular to the vertical movement direction while balancing the inertial force of the action device in the vertical direction, thereby causing vibration side effects again.
  • the saw is provided with another counterweight device for balancing the inertial force component generated by the eccentric mass in the horizontal direction.
  • a power tool which may include a rotating wheel that is driven to rotate about a central axis thereof; an actuating member for carrying a tool of the power tool; and a weight member, wherein a rotating wheel driven to rotate about a central axis to drive the actuating member to reciprocate linearly in a first direction while driving the weight member to reciprocate in a direction opposite to the actuating member in the first direction
  • the movement performs a reciprocating oscillating movement in a plane perpendicular to the central axis, said first direction being parallel to said plane.
  • the weight member does not perform a rotational motion, but performs a reciprocating swing motion while performing a linear motion opposite to the motion member of the power tool.
  • the center of mass of the weight member moves along an elliptical trajectory. Since the oscillating motion has a motion component in a direction perpendicular to the moving direction of the action member, the weight member also generates an inertial force component in the vertical direction, in order to balance the inertial force component in the vertical direction of the weight member, according to
  • the rotating wheel of the power tool of the invention is preferably designed in the form of an eccentric.
  • the centrifugal resultant force received by the rotating wheel during the rotation has a first rigid force component in a direction opposite to a direction of the inertial force of the actuating member and a second inertial force component in the vertical direction.
  • the first rigid force component of the eccentric rotating wheel is used together with the inertial force of the weight member to balance the inertial force of the actuating member, and the second rigid force component of the eccentric rotating wheel is used to balance the inertia of the weight member in the vertical direction. Force component.
  • the inertial force of the action device in the reciprocating direction is effectively balanced by providing the weight member, and the balance wheel member is arranged in an eccentric structure to effectively balance the weight member in the direction perpendicular to the movement direction. Inertia force in the vertical direction.
  • the inertial force components of the weight member and the rotating wheel are in the same direction and superimposed on each other, and the vibration generated by the action device can be balanced together; in the vertical direction, the inertia force of the weight member and the rotating wheel The components are opposite in direction and cancel each other, and the vibration in the vertical direction can be reduced or eliminated.
  • This structure effectively reduces the vibration generated by the power tool and prevents the power tool from damaging the internal components due to the vibration, which prolongs the service life of the power tool and enables the operator to operate comfortably.
  • Figure 1 is an exploded perspective view of a portion of a jig saw in accordance with the present invention
  • Figure 2 is an assembled perspective view of a portion of a jig saw in accordance with the present invention.
  • Figure 3 is a front elevational view, respectively, of a portion of a jig saw in accordance with the present invention.
  • Figure 4 shows a side view of a portion of a jig saw according to the present invention, respectively;
  • Figure 5 shows a rear view of a portion of a jig saw according to the present invention, respectively;
  • Figures 6a-6b show side and front views of one example of a rotating wheel of a jig saw of the present invention
  • FIG. 7a-7b are front and side views showing an example of a support frame of a jigsaw of the present invention.
  • FIGS. 8a-8b are front and perspective views showing an example of a weight member of a jig saw of the present invention.
  • Fig. 9 shows a force relationship diagram corresponding to the position in Fig. 5.
  • the term "power tool” includes, but is not limited to, a reciprocating chainsaw such as a jig saw, a hammer, and the like.
  • a reciprocating chainsaw such as a jig saw, a hammer, and the like.
  • Other types of portable power tools that can be adapted to the principles of the present invention are also included within the scope of the present invention, and the scope of the present invention is not limited in any way to the detailed structures and forms illustrated in the drawings and described herein. It is only limited by the claims.
  • a power tool in general, includes a driving device that outputs a rotational motion, an action device that performs a reciprocating linear motion in a linear motion direction, and a motion conversion mechanism that converts a rotational motion from the drive assembly into a reciprocating linear motion of the output assembly.
  • the power tool of the present invention employs a new type of motion conversion mechanism.
  • the novel motion conversion mechanism of the present invention mainly includes a rotating wheel driven by a driving device and a weight member driven by the rotating wheel.
  • the rotating wheel is driven to rotate about its own rotation axis by the driving device, and the rotating rotating wheel performs a reciprocating linear motion by the action device that drives the power tool by the first driving portion, and drives the weight member to move by the second driving portion.
  • the rotating wheel is configured as an eccentric rotating wheel such that the inertial force generated by the rotation of the eccentric rotating wheel has a first inertial force component in the linear motion direction and a second inertial force component in a vertical direction perpendicular to the direction.
  • the weight member includes a frame joint that is offset from its center of mass, and the rotating rotating wheel drives the weight member, and on the one hand, the entire weight member is in the linear motion direction relative to the frame of the power tool through its frame joint
  • the upper reciprocating slide is opposite to the action device, and on the other hand the entire weight member is pivoted about the frame joint.
  • the frame engaging portion is located between an centroid of the weight member and a corresponding engaging portion engaged with the second driving portion of the rotating wheel, and moves along an elliptical path, such that the weight member moves in the linear motion direction
  • the component produces a third inertial force component
  • the pivoting motion of the weight member also produces a fourth inertial force component in the vertical direction.
  • the first inertial force component of the rotating wheel and the third inertial force component of the weight member are both in the linear motion direction and opposite to the inertial force direction of the action device of the power tool, so that the inertial force of the action device is balanced.
  • the second inertial force component of the rotating wheel and the fourth inertial force component of the weight member are equal in magnitude and opposite in direction in the vertical direction, and cancel each other to achieve the purpose of eliminating vibration in the vertical direction.
  • the linear motion direction is a vertical direction
  • the vertical direction is a horizontal direction perpendicular to the vertical direction.
  • first direction herein means the direction of the reciprocating linear motion of the action device of the electric power tool
  • second direction indicates the direction perpendicular to the first direction.
  • FIG. 1 and 2 show an exploded view and an assembled view, respectively, of a portion of jigsaw 100
  • Figs. 3 through 5 show front, side and rear views, respectively, of a portion of jigsaw 100.
  • the frame of jigsaw 100 in the figures is removed to clearly show the internal functional components of jigsaw 100.
  • the drive of the jigsaw 100 is not shown.
  • the drive can be any type of drive known in the art, such as a motor that outputs rotational motion through the output shaft 10.
  • the output shaft 10 is also supported by a support 20 that is fixed to the frame of the jigsaw 100.
  • the support 20 is for example, but not limited to, the form of a support plate as shown.
  • the actuating device comprises an actuating member 30 supporting a tool holder 35, wherein the tool holder 35 is used to hold the tool of the jigsaw 100, in particular the saw blade 37.
  • the actuating member 30 is configured to reciprocally move linearly relative to the frame of the power tool in the first direction D1.
  • the novel motion conversion mechanism of the present invention includes a rotating wheel 40 driven by the output shaft 10 of the driving device and a weight member 50 driven by the rotating wheel 40.
  • the rotary wheel 40 has a central support hole 42 through which the wheel support shaft 24 extending from the support member 20 supports the rotary wheel 40 to enable the rotary wheel 40 to rotate about a central axis X1 defined by the support hole 42.
  • the rotating wheel 40 defines a first side 40a facing the actuating member 30 and an opposite second side 40b, and includes a first extending from the first side 40a toward the actuating member 30.
  • the protrusion 44 and the second protrusion 46 projecting away from the action member 30 from the second side 40b.
  • the first projection 44 is adapted to be received within a bore 32 formed in the actuating member 30.
  • the second projection 46 is adapted to be received within a bore 52 formed in the weight member 50.
  • the weight member 50 defines a first side 50a facing the rotating wheel 40, ie towards the actuating member 30, and an opposite second side 50b, the hole 52 from the first One side 50a is recessed into the weight member 50.
  • the aperture 52 can extend from the first side 50a to the second side 50b to define a through hole. Alternatively, the aperture 52 may not extend through the weight member 50.
  • the weight member 50 also includes a projection 54 extending from a second side 50b thereof, the projection 54 being received within a bore 22 formed in the support member 20, the bore 22 being elongated in a first direction D1.
  • the first projection 44 and the second projection 46 of the rotating wheel 40 are located on opposite sides of the diametrical direction of the rotating wheel 40, i.e., diagonally Arranged. Furthermore, the rotating wheel 40 is specifically designed such that its center of mass 45 is offset from the central axis 44 defined by the central bore 42 away from the first projection 44.
  • the geometric center of the second protrusion 46, the geometric center of the first protrusion 44, and the centroid 45 of the rotating wheel 40 are projected on the orthogonal plane and the intersection X is on a common line, thus
  • the geometric center of the second projection 46, the geometric center of the first projection 44, and the center of mass 45 of the rotating wheel 40 and the central axis X1 of the rotating wheel 40 are all located in a common plane perpendicular to the orthogonal plane.
  • the eccentric rotating wheel 40 can be realized by at least one of the following: the mass of the second protrusion 46 extending from the second side 40b is greater than the mass of the first protrusion 44 extending from the first side 40a; One or more recesses or through holes 48 are provided on a side of the rotating wheel 40 adjacent to the first protrusion 44 to reduce the mass of the side of the first protrusion 44; added on one side of the second protrusion 46 The protrusion increases the mass of the side of the second protrusion 46.
  • two through holes 48 are provided that are mirrored relative to the common plane containing the common line.
  • any other means than the ones listed above can be employed.
  • the center of mass 55 of the weight member 50 is offset from the center of the aperture 52 of the second projection 46 of the receiving rotary wheel 40 and from the center of the projection 54.
  • the projections of the center of the centroid 55 and the hole 52 in the above-mentioned orthogonal plane or a plane parallel to the orthogonal plane are respectively located at the center of the protrusion 54 in the above-mentioned orthogonal plane or with the above-mentioned orthogonal plane. Opposite sides of the projection on parallel planes.
  • this can be achieved by at least one of the following ways: increasing the size of the aperture 52 to reduce the mass on one side of the aperture 52; increasing the mass on the side opposite the aperture 52.
  • any other structure that allows the centroid 55, the projections 54, and the holes 52 to have the above-described positional relationship can be employed.
  • the output shaft 10 of the driving device drives the rotary wheel 40 to rotate about its central axis X1
  • it is disposed on the opposite sides of the central axis X1 of the rotary wheel 40, and deviates from its central axis X1.
  • the first protrusion 44 and the second protrusion 46 revolve around the central axis X1 of the rotary wheel 40, respectively, while driving the action member 30 and the weight member 50 to move, respectively.
  • the motion component in the first direction D1 causes the first protrusion 44 to push the actuating member 30 to move in the first direction D1, in the vertical direction.
  • the motion component in the second direction D2 of the first direction D1 causes the first protrusion 44 to slide within the aperture 32 of the actuating member 30.
  • the second projection 46 is moved about the central axis X1 of the rotary wheel 40 to drive the weight member 50, and the hole 52 of the weight member 50 is rotated about the central axis X1 of the rotary wheel 40.
  • the projection 54 of the weight member 50 slides along the aperture 22 of the support member 20 in the first direction D1, and on the other hand, the weight member 50 pivots about the projection 54, in particular by the projection 54.
  • the axis pivots, in particular to oscillate.
  • the first protrusion 44 is driving the actuating member 30 to move downward, at the center with respect to the rotating wheel 40.
  • the second protrusion 46 is driving the weight member 50 to move, at which time the weight member 50 is pivoting about the protrusion 54 while moving upward, and the center of mass 55 of the weight member 50 is at the right upper left. motion.
  • Fig. 9 shows a force relationship diagram corresponding to the position shown in Fig. 5.
  • the rotary wheel 40 rotates clockwise, so that the first projection 44 and the actuating member 30 of the jigsaw 100 are about to be moved from the intermediate position of the reciprocating motion to the lowermost position, and the action member is decelerated downward.
  • the acceleration direction is upward, since the inertial force direction is opposite to the acceleration direction, the inertial force F30 of the actuating member 30 is downward; for the rotating wheel 40, the inertial centrifugal force F40 at the center of mass 45 is directed to the upper left;
  • the weight member 50 since the second protrusion 46 of the driving weight member 50 is opposite to the direction of movement of the first protrusion 44 of the driving action member 30, the weight member 50 is about to be moved from the intermediate position of the reciprocating motion to the uppermost position.
  • the upward deceleration motion the acceleration is downward, so there is an upward inertial force component F51; at the same time, its centroid 55 is about to move from the rightmost position to the middle position of the left and right swings, accelerates to the left, and the acceleration is to the left, so there is inertia to the right.
  • the force component F52 has a total inertial force F50 at its center of mass 55 in the upper right direction.
  • the component F41 of the inertial force F40 of the rotating wheel 40 in the first direction D1 is the same as the component F51 of the inertial force F50 of the weight member 50 in the first direction D1, both in the first direction with the actuating member 30.
  • the inertial force F30 on D1 is opposite in direction, so the inertial force F30 of the actuating member 30 is in the first direction D1 by the component F41 of the inertial force F40 of the rotating wheel 40 in the first direction D1 and the inertial force F50 of the weight member 50.
  • the sum of the components F51 is balanced.
  • the component F42 of the inertial force F40 of the rotating wheel 40 in the direction is opposite to the component F52 of the inertial force F50 of the weight member 50 in the direction, which cancel each other.
  • the rotating wheel 40 and the weight member 50 are rotated at any position of the rotating wheel 40.
  • the components of the inertial force in the first direction D1 are all in the same direction, and the sum of the two is offset from the inertial force in the direction of the actuating member 30. From this point of view, the balance member is simply balanced by the weight member. Compared with the existing structure of the inertial force, the required weight of the weight member is greatly reduced, and the quality of the power tool is correspondingly reduced.
  • the components of the inertial force of the rotating wheel 40 and the weight member 50 in the second direction D2 are opposite in direction and equal in magnitude, and the two cancel each other. From this point of view, in order to manufacture the eccentric rotating wheel that realizes this function, the rotating wheel can be removed. Part of the material, such as the holes 48 in the figure, alleviates the quality of the rotating wheel and correspondingly reduces the quality of the power tool. Meanwhile, as described above, most importantly, the inertial force of the moving parts of the jigsaw 100 having such a structure in both the first direction and the second direction is balanced, and the vibration which may be generated is reduced or even eliminated.
  • the weight member 50 slides in the first direction D1 and pivots around the projection 54.
  • the weight member 50 can also include another feature that can be pivotable and slidable relative to the frame of the jigsaw 100.
  • the other feature is a circular arc-shaped outer contour 58 that is concentric with the center of the cylinder forming the projection 54, such as two circular outer contours 58 that oppose each other.
  • an engagement portion 82 for receiving the circular arc-shaped outer contour 58 can also be formed on the support 20 so that the weight 50 can be in the circle
  • the curved outer contour 58 abuts in the receiving portion 82 in a manner that slides relative to the frame 80 of the jigsaw 100 in the first direction D1 and enables the weight member 50 to pivot about the center of the arcuate outer contour 58.
  • the weight member 50 can function as the same principle as described above.
  • the power tool of the present invention described by the jigsaw 100 as an example effectively balances the inertial force of the actuating member 30 in the reciprocating direction by providing the weight member 50, and is effectively balanced by setting the rotating wheel 40 to an eccentric structure.
  • the inertial force of the weight member 50 in the vertical direction perpendicular to the direction of motion.
  • This structure effectively reduces the vibration generated by the power tool and prevents the power tool from damaging the internal components due to the vibration, which prolongs the service life of the power tool and enables the operator to operate comfortably.
  • the jigsaw 100 can include at least one of the following features:
  • the support portion 20 is not limited to the illustrated plate member, but may have any structural form, and may alternatively be a part of the frame of the jigsaw 100;
  • the shape, number, and arrangement of the apertures 48 of the rotating wheel 40 can vary from the shapes, numbers, and arrangements illustrated;
  • the hole 48 in the rotating wheel 40, the hole 32 in the actuating member 30, the hole 52 in the weight member 50, and the hole 22 in the support member 20 may be through holes, optionally any of them. Can be a non-through hole;
  • first protrusion 44, the second protrusion 46, and the protrusion 54 are all illustrated as cylindrical protrusions, but those skilled in the art understand that any other optional structure having the same function can also be employed;
  • the weight member can include a protrusion and the rotating wheel can include an aperture that receives the protrusion.

Abstract

一种电动工具，包括：被驱动而绕自身的中心轴线（X1）旋转的旋转轮（40），用于承载电动工具的刀具的动作件（30），以及配重件（50）。其中，被驱动而绕中心轴线（X1）旋转的旋转轮（40）驱动动作件（30）使其沿第一方向（D1）往复直线运动，同时驱动配重件（50）使其，一方面沿第一方向（D1）与动作件（30）相反地往复直线运动，另一方面在垂直于中心轴线（X1）的平面中进行往复摆动运动，第一方向（D1）平行于所述平面。

Description

电动工具 技术领域.
本申请涉及电动工具领域，尤其涉及输出往复直线运动的电动工具。
背景技术
常见的电动工具，例如往复锯、电锤等，包括输出旋转运动的驱动装置，输出往复直线运动的动作装置，以及将驱动装置的旋转运动转换为动作装置的往复直线运动的运动转换机构。
这种类型的电动工具的动作装置通过执行往复直线运动而对目标工件进行往复冲击或往复切割等操作。动作装置在被驱动而进行往复直线运动时会频繁进行运动方向的改变，频繁改变运动方向的动作装置由于惯性作用使电动工具产生振动，进而降低电动工具的使用寿命；也容易对操作人员带来生理上的疲劳性损伤，同时也影响操作人员操作电动工具的舒适性。
为了减小电动工具的振动，从而获得理想的操作性能，本领域内的技术人员已经做了许多努力。
例如，现有技术中存在一种曲线锯，为了平衡其动作装置在竖直方向上进行往复直线运动而产生的惯性力，在旋转轮上设有附加偏心质量，此偏心质量随旋转轮一起绕旋转轮的旋转轴线进行旋转。
再例如，现有技术中还有一种往复式锯，首先，其包括类似于如上述的偏心质量，用来平衡电动工具的动作装置在运动方向上产生的惯性力，消除由此惯性力所产生的振动。然而，此偏心质量在平衡动作装置在竖直方向上的惯性力的同时，在垂直于竖直运动方向的水平方向上产生力分量，进而再次引发振动副作用。为了进一步减小在操作过程中由于偏心质量引发的振动副作用，该锯还设有另一配重装置，该另一配重装置用来平衡所述偏心质量在水平方向上产生的惯性力分量。
发明内容
本发明的目的是提供一种具有降低振动功能的新式电动工具结构，或 者至少为使用者提供一种选择。
为此，根据本发明，提供了一种电动工具，其可包括被驱动而绕自身的中心轴线旋转的旋转轮；用于承载所述电动工具的刀具的动作件；以及配重件，其中，被驱动而绕中心轴线旋转的旋转轮驱动所述动作件使其沿第一方向往复直线运动，同时驱动配重件使其，一方面沿所述第一方向与所述动作件相反地往复直线运动，另一方面在垂直于中心轴线的平面中进行往复摆动运动，所述第一方向平行于所述平面。
在本发明的新式电动工具结构中，其配重件不是进行旋转运动，而是在与电动工具的动作件相反地进行直线运动的同时，进行往复摆动运动。特别地，配重件的质心沿一椭圆形轨迹运动。由于所述摆动运动存在与动作件的运动方向垂直的方向上的运动分量，所以配重件同样产生垂直方向上的惯性力分量，为了平衡配重件的此垂直方向上的惯性力分量，根据本发明的电动工具的旋转轮优选被设计为偏心轮的形式。所述旋转轮在旋转过程中受到的离心合力具有与所述动作件的惯性力的方向相反的方向上的第一刚性力分量和在所述垂直方向上的第二惯性力分量。偏心旋转轮的第一刚性力分量与配重件的惯性力一起用来平衡动作件的惯性力，而偏心旋转轮的第二刚性力分量则用来平衡配重件在该垂直方向上的惯性力分量。
根据本发明的新式电动工具，通过提供配重件而使动作装置在往复运动方向上的惯性力得到有效平衡，通过将旋转轮设置成偏心结构有效地平衡了配重件在垂直于运动方向的垂直方向上的惯性力。这样，在动作件的往复运动方向上，配重件和旋转轮的惯性力分量方向相同、相互叠加，可以共同平衡动作装置产生的振动；在垂直方向上，配重件和旋转轮的惯性力分量方向相反、相互抵消，可以减小或消除垂直方向上的振动。这种结构有效地降低了电动工具产生的振动，避免电动工具因为产生振动而导致内部部件破坏，既延长了电动工具的使用寿命，又使得操作人员能够舒适地进行操作。
附图说明
从下面结合附图描述的、本申请的优选实施例中可以更好地理解本申请的上述和其它特征和优势，其中：
图1是根据本发明的曲线锯的一部分的分解立体图；
图2是根据本发明的曲线锯的一部分的组装立体图；
图3分别示出了根据本发明的曲线锯的一部分的正视图；
图4分别示出了根据本发明的曲线锯的一部分的侧视图；
图5分别示出了根据本发明的曲线锯的一部分的后视图；
图6a-6b示出了本发明的曲线锯的旋转轮的一个例子的侧视图和正视图；
图7a-7b示出了本发明的曲线锯的支撑架的一个例子的正视图和侧视图；和
图8a-8b示出了本发明的曲线锯的配重件的一个例子的正视图和立体图；
图9示出了与图5中的位置对应的力关系图。
具体实施方式
在本文中，术语“电动工具”包括，但不仅限于，往复式电锯、比如曲线锯，电锤等。能够适用于本发明的原理的其它类型的便携式电动工具也被包含在本发明的范围内，本发明的保护范围不以任何方式限制于图中示出的和在这里描述的详细结构和形式，而是仅通过权利要求书限定。
总体上，根据本发明的电动工具包括输出旋转运动的驱动装置，沿一直线运动方向执行往复直线运动的动作装置，以及将来自驱动组件的旋转运动转换为输出组件的往复直线运动的运动转换机构。为了避免或最大程度地降低由于进行往复直线运动的动作装置的惯性力而引起电动工具的振动，本发明的电动工具采用了一种新式运动转换机构。
本发明的新式运动转换机构主要包括被驱动装置驱动的旋转轮和被旋转轮驱动的配重件。旋转轮通过驱动装置驱动而绕自身的旋转轴线自转，旋转的旋转轮通过第一驱动部驱动电动工具的动作装置执行往复直线运动，通过第二驱动部驱动配重件进行运动。旋转轮被构造成偏心旋转轮，从而偏心旋转轮的旋转产生的惯性力在所述直线运动方向上具有第一惯性力分量、在垂直于该方向的垂直方向上具有第二惯性力分量。
配重件包括从其质心偏离的一机架接合部，旋转的旋转轮驱动配重件，一方面通过其机架接合部使整个配重件相对于电动工具的机架在所述直线运动方向上与动作装置相反地往复滑动，另一方面使整个配重件绕所述机 架接合部枢转。所述机架接合部位于配重件的质心和与旋转轮的第二驱动部接合的对应接合部之间，沿一椭圆形轨迹运动，这样，配重件在所述直线运动方向上的运动分量产生第三惯性力分量，配重件的枢转运动还产生在所述垂直方向上的第四惯性力分量。
旋转轮的第一惯性力分量和配重件的第三惯性力分量都在所述直线运动方向上，并且与电动工具的动作装置的惯性力方向相反，使动作装置的惯性力得以平衡。旋转轮的第二惯性力分量和配重件的第四惯性力分量在所述垂直方向上大小相等、方向相反，互相抵消，达到消除垂直方向上的振动的目的。
下面以曲线锯为例、参考附图详细说明根据本发明的电动工具的工作原理。在图示的曲线锯例子中，所述直线运动方向是竖直方向，所述垂直方向为垂直于竖直方向的水平方向。为方便起见，本文中以“第一方向”表示电动工具的动作装置的往复直线运动方向，以“第二方向”表示与第一方向垂直的方向。
图1和图2分别示出了曲线锯100的一部分的分解图和装配图，图3至5分别示出了曲线锯100的一部分的正视图、侧视图和后视图。附图中曲线锯100的机架被移除以清楚地显示出曲线锯100的内部功能部件。
为了突出显示本发明的创新性方面，曲线锯100的驱动装置未示出。但是，本领域内的技术人员应了解该驱动装置可以是本领域内已知的任何类型的驱动装置，例如电机，其通过输出轴10输出旋转运动。输出轴10还通过固定到曲线锯100的机架上的支撑件20支撑。支撑件20例如是、但不仅限于图中示出的支撑板的形式。
在附图示出的曲线锯100中，动作装置包括支撑着刀具保持架35的动作件30，其中刀具保持架35用于保持曲线锯100的刀具，具体为锯条37。动作件30被配置为相对于电动工具的机架沿着第一方向D1往复直线运动。
本发明的新式运动转换机构包括被驱动装置的输出轴10驱动的旋转轮40和被旋转轮40驱动的配重件50。
旋转轮40具有居中的支撑孔42，从支撑件20伸出的轮支撑轴24穿过支撑孔42而支撑着旋转轮40，使旋转轮40能够绕由支撑孔42限定的中心轴线X1旋转。
在旋转轮40的中心轴线X1的方向上，旋转轮40限定出朝向动作件 30的第一侧40a和相反的第二侧40b，并且包括从第一侧40a朝向动作件30伸出的第一突部44和从第二侧40b背离动作件30伸出的第二突部46。第一突部44适于被接收在形成于动作件30上的孔32内。第二突部46适于被接收在形成于配重件50上的孔52内。
如图所示，在旋转轮40的中心轴线X1的方向上，配重件50限定出朝向旋转轮40、即朝向动作件30的第一侧50a和相反的第二侧50b，孔52从第一侧50a凹入到配重件50内，如图所示，孔52可以从第一侧50a延伸到第二侧50b从而限定出贯穿孔，可选地孔52也可以不贯穿配重件50的本体。配重件50还包括从其第二侧50b伸出的突部54，突部54被接收在形成于支撑件20上的孔22内，孔22沿着第一方向D1伸长。
根据本发明的新颖性方面，如图6a-6b所示，旋转轮40的第一突部44和第二突部46位于旋转轮40的直径方向上的相反两侧，即以对角方式对置布置。此外，旋转轮40被特别地设计为使其质心45从由中心孔42限定的中心轴线远离第一突部44偏离。也就是说，如6b的侧视图所示，在垂直于旋转轮40的中心轴线X1的正交平面中，在经过旋转轮40的中心轴线X1与所述正交平面的交点X的直径方向上，第二突部46的几何中心在该正交平面上的投影和旋转轮40的质心45在该正交平面上的投影两者都位于第一突部44的几何中心在该正交平面上的投影关于所述交点X的相反侧。最佳地，第二突部46的几何中心、第一突部44的几何中心和旋转轮40的质心45三者在该正交平面上的投影以及所述交点X在一公共直线上，因此，第二突部46的几何中心、第一突部44的几何中心和旋转轮40的质心45以及所述旋转轮40的中心轴线X1都位于垂直于该正交平面的一公共平面中。
具体地，偏心旋转轮40可以通过如下方式中至少一者实现：使从第二侧40b伸出的第二突部46的质量大于从第一侧40a伸出的第一突部44的质量；在旋转轮40的靠近第一突部44的一侧设置一个或多个凹陷部或者贯穿孔48，以减轻第一突部44的那一侧的质量；在第二突部46的一侧添加突部以增大第二突部46那一侧的质量。在图示实施例中，设置有相对于包含所述公共直线的所述公共平面镜像设置的两个贯穿孔48。当然，除上述列出的方式之外的任何其它方式都可以采用。
根据本发明的新颖性方面，如图8a-8b所示，配重件50的质心55从接 收旋转轮40的第二突部46的孔52的中心以及从突部54的中心偏离。对于配重件50来说，质心55与孔52的中心在上述正交平面或与上述正交平面平行的平面上的投影分别位于突部54的中心在上述正交平面或与上述正交平面平行的平面上的投影的相反两侧。例如，这可以通过如下方式中的至少一种方式实现：增大孔52的大小以减小孔52一侧的质量；增大与孔52相反的一侧的质量。当然，使质心55、突部54以及孔52具有上述位置关系的任何其它结构都可以采用。
利用如上所述的结构，当驱动装置的输出轴10驱动旋转轮40使其绕其中心轴线X1旋转时，设置于旋转轮40的中心轴线X1的相反两侧上、并且从其中心轴线X1偏离的第一突部44和第二突部46分别绕旋转轮40的中心轴线X1公转，同时分别驱动动作件30和配重件50运动。
在第一侧40a，第一突部44绕旋转轮40的中心轴线X1公转时，在第一方向D1上的运动分量致使第一突部44推动动作件30沿第一方向D1运动，在垂直于第一方向D1的第二方向D2上的运动分量致使第一突部44在动作件30的孔32内滑动。
在第二侧40b，第二突部46绕旋转轮40的中心轴线X1公转时驱动配重件50运动，配重件50的孔52绕旋转轮40的中心轴线X1旋转。同时，一方面配重件50的突部54沿支撑件20的孔22在第一方向D1上滑动，另一方面，配重件50绕突部54、具体为由突部54限定的枢转轴线枢转，特别地进行摆动。
例如，参考图5(和下文受力分析一致)，以旋转轮40绕顺时针R旋转为例，第一突部44正在驱动动作件30使其向下移动，在相对于旋转轮40的中心轴线X1的相反一侧，第二突部46正在驱动配重件50运动，此时配重件50在向上移动的同时正在绕突部54枢转，配重件50的质心55在朝右左上方运动。
图9示出了与图5所示位置对应的力关系图。如图9所示，在该时刻，旋转轮40顺时针旋转，因此第一突部44、以及曲线锯100的动作件30即将由往复运动的中间位置运动到最下位置，动作件减速向下运动，加速度方向向上，由于惯性力方向与加速度方向相反所以动作件30的惯性力F30方向为向下；对于旋转轮40来说，在其质心45处的惯性离心力F40朝向左上方；对于配重件50来说，由于驱动配重件50的第二突部46与驱动动 作件30的第一突部44运动方向正好相反，所以配重件50即将由往复运动的中间位置运动到最上位置，向上减速运动，加速度向下，所以有向上的惯性力分量F51；同时，其质心55即将由最右位置运动到左右摆动的中间位置，向左加速运动，加速度向左，所以有向右的惯性力分量F52，在其质心55处的总的惯性力F50方向为右上方。
由此可知，旋转轮40的惯性力F40在第一方向D1上的分量F41与配重件50的惯性力F50在第一方向D1上的分量F51方向相同，都与动作件30在第一方向D1上的惯性力F30方向相反，所以动作件30的惯性力F30通过旋转轮40的惯性力F40在第一方向D1上的分量F41与配重件50的惯性力F50在第一方向D1上的分量F51两者之和来平衡。在第二方向D2上，旋转轮40的惯性力F40在该方向上的分量F42与配重件50的惯性力F50在该方向上的分量F52相反，二者相互抵消。
所以，根据本发明的原理，通过合理的设置旋转轮40和配重件50的质心位置，在曲线锯100操作的任何时刻，在旋转轮40旋转的任何位置，旋转轮40和配重件50的惯性力在第一方向D1上的分量都方向相同，二者之和与动作件30的该方向上的惯性力进行抵消，从这个角度来讲，与单单由配重件来平衡动作件的惯性力的现有结构相比，所需的配重件质量大大减小，相应地减轻了电动工具的质量。旋转轮40和配重件50的惯性力在第二方向D2上的分量方向相反，大小相等，二者相互抵消，从这个角度来讲，为了制造实现此功能的偏心旋转轮，可以去除旋转轮的部分材料，例如图中的孔48，这减轻了旋转轮的质量，相应地也减轻了电动工具的质量。同时，如上述，最重要地，具有这种结构的曲线锯100的运动部件在第一方向和第二方向上的惯性力都得到平衡，减小、甚至消除了可能产生的振动。
在本发明的结构中，通过设置被支撑件20的长孔22接收的突部54，配重件50既沿第一方向D1滑动又围绕突部54枢转。作为可选特征或作为附加特征，配重件50还可以包括能够相对于曲线锯100的机架可枢转并且可滑动的另一特征。在图示的实施例中，该另一特征是与形成突部54的柱体的中心同心的圆弧形外轮廓58，例如彼此对置的两个圆弧形外轮廓58。与此相对应地，在曲线锯100的机架80上、例如也可以在支撑件20上形成用于接收该圆弧形外轮廓58的接合部82，使得配重件50能够以所述圆 弧形外轮廓58抵接于该接收部82内的形式相对于曲线锯100的机架80在第一方向D1上滑动并且使配重件50能够绕圆弧形外轮廓58的中心枢转。这样，配重件50能够以如上述相同的原理发挥作用。
以曲线锯100作为例子描述的本发明的电动工具，通过提供配重件50而使动作件30在往复运动方向上的惯性力得到有效平衡，通过将旋转轮40设置成偏心结构有效地平衡了配重件50在垂直于运动方向的垂直方向上的惯性力。这种结构有效地降低了电动工具产生的振动，避免电动工具因为产生振动而导致内部部件破坏，既延长了电动工具的使用寿命，又使得操作人员能够舒适地进行操作。
作为曲线锯100的上述优选实施例的替代实施方式，曲线锯100可包括下述特征中的至少一个：
支撑部20不限制于图示的板状件，而是可以具有任何结构形式，可选地，其可以是曲线锯100的机架的一部分；
旋转轮40的孔48的形状、数量和布置方式可以不同于图示的形状、数量和布置方式；
旋转轮40上的孔48，动作件30上的孔32，配重件50上的孔52以及支撑件20上的孔22中任一者都可以是贯穿孔，可选地其中的任一者可以是非贯穿孔；
为简单起见，第一突部44、第二突部46和突部54都图示为圆柱形突部，但本领域内的技术人员理解还可以采用具有相同功能的任何其它可选结构；
作为第二突部46和孔52的替代实施方式，配重件可包括突部，旋转轮可包括接纳突部的孔。
上面关于本发明的优选实施例进行了描述，但本发明并不意于限制于上面描述和附图示意的实施例。在不偏离由下面的权利要求限定的实质和范围的情况下，本领域内的技术人员可以对上述实施例的结构细节和形式进行各种修改和变异。

Claims (10)

  1. 一种电动工具，包括：
    被驱动而绕自身的中心轴线(X1)旋转的旋转轮(40)；用于承载所述电动工具的刀具的动作件(30)；以及配重件(50)，
    其中，被驱动而绕中心轴线(X1)旋转的旋转轮(40)驱动所述动作件(30)使其沿第一方向(D1)往复直线运动，同时驱动配重件(50)使其，一方面沿所述第一方向(D1)与所述动作件(30)相反地往复直线运动，另一方面在垂直于中心轴线(X1)的平面中进行往复摆动运动，所述第一方向(D1)平行于所述平面。
  2. 根据权利要求1所述的电动工具，其中，所述往复摆动运动绕垂直于所述平面的一枢转轴线进行。
  3. 根据权利要求2所述的电动工具，其中，所述配重件(50)包括能够相对于电动工具的机架滑动的滑动部，所述滑动部限定所述枢转轴线。
  4. 根据权利要求3所述的电动工具，其中，所述滑动部包括从配重件(50)伸出的突出部，所述突出部的中心位于所述枢转轴线上，相应地，所述机架具有适于接收所述突出部的长槽，所述长槽沿所述第一方向(D1)延伸，和/或
    所述滑动部包括配重件(50)的弧形外轮廓，所述弧形外轮廓的中心位于所述枢转轴线上，相应地，所述机架具有构造成使所述弧形外轮廓抵靠着沿所述第一方向(D1)直线运动的配合部。
  5. 根据权利要求2-4中任一项所述的电动工具，其中，所述旋转轮(40)包括驱动所述配重件(50)的配重件驱动部，所述配重件(50)包括与所述配重件驱动部接合的驱动接合部，并且，在所述平面中，所述枢转轴线与所述平面中的交点位于所述配重件(50)的质心(55)在所述平面上的投影与所述驱动接合部的中心在所述平面中的投影之间。
  6. 根据权利要求1-4中任一项所述的电动工具，其中，所述旋转轮(40)是偏心轮，所述旋转轮(40)在旋转过程中受到的离心合力具有与所述动作件(30)的惯性力的方向相反的方向上的力分量和在垂直于第一方向(D1)的第二方向(D2)上的力分量。
  7. 根据权利要求5所述的电动工具，其中，所述旋转轮(40)还包括驱动所述动作件(30)的动作件驱动部，所述配重件驱动部的中心和旋转轮(40)的质心(45)在所述平面上的投影都位于所述动作件驱动部的中心在所述平面上的投影相对于旋转轮(40)的中心轴线(X1)与所述平面的交点(X)的相反侧。
  8. 根据权利要求7所述的电动工具，其中，在相对于所述旋转轮(40)的中心轴线(X1)来说靠近动作件驱动部的那一侧上，所述旋转轮(40)被形成有凹部或孔，使所述旋转轮具有通过凹部或孔形成的质量偏心结构。
  9. 根据权利要求7所述的电动工具，其中，所述动作件驱动部和所述配重件驱动部都直接从旋转轮(40)伸出。
  10. 根据权利要求1-9中任一项所述的电动工具，其中，所述电动工具是往复式锯。
PCT/CN2018/087955 2017-05-31 2018-05-23 电动工具 WO2018219184A1 (zh)

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