WO2019233380A1 - 动力工具 - Google Patents

动力工具 Download PDF

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Publication number
WO2019233380A1
WO2019233380A1 PCT/CN2019/089844 CN2019089844W WO2019233380A1 WO 2019233380 A1 WO2019233380 A1 WO 2019233380A1 CN 2019089844 W CN2019089844 W CN 2019089844W WO 2019233380 A1 WO2019233380 A1 WO 2019233380A1
Authority
WO
WIPO (PCT)
Prior art keywords
vibration isolation
vibration
plane
power tool
motor
Prior art date
Application number
PCT/CN2019/089844
Other languages
English (en)
French (fr)
Inventor
凌齐
王荣
李阳
Original Assignee
南京德朔实业有限公司
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 CN201811442212.XA external-priority patent/CN110561355B/zh
Application filed by 南京德朔实业有限公司 filed Critical 南京德朔实业有限公司
Priority to EP19814032.9A priority Critical patent/EP3815847B1/en
Publication of WO2019233380A1 publication Critical patent/WO2019233380A1/zh
Priority to US17/112,530 priority patent/US11027349B2/en

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Classifications

    • 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
    • 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
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for
    • B25F5/02—Construction of casings, bodies or handles

Definitions

  • This article relates to a power tool, such as a swing type tool.
  • Power tools such as electric hammers, reciprocating saws, and swing tools generate vibration during the work process, which will affect the machining effect of the workpiece being processed.
  • This type of hand-held power tools is held by users when they hold them for work.
  • the vibration generated by the tool itself will be transmitted to the user through the human hand, so that the user cannot hold the tool stably, and it will also make the user feel tired after working for a period of time.
  • swinging tools it includes an eccentric transmission assembly for swinging, so that swinging tools have a large vibration after turning on.
  • this paper provides a power tool with good damping effect.
  • a power tool includes: a power component including a motor, the motor including a motor shaft rotatable about a motor axis; an output component including an output shaft configured to output power; a transmission component configured to be implemented between the power component and the output component Power transmission; the first housing can support at least the power component, the transmission component and the output component; the second housing surrounds at least part of the first housing, and the second housing is also formed with a structure for holding by the user A handle part; wherein, the power tool is provided with a first vibration isolation plane and a second vibration isolation plane, a first vibration isolation block is provided on the first vibration isolation plane, and a second vibration isolation block is provided on the second vibration isolation plane; The whole of the vibration isolating block and the second vibration isolating block has at least a space portion provided between the first case and the second case, and the second case is spaced apart from the first case at the space portion; the first The vibration isolation block and the second vibration isolation block are separated from each other.
  • FIG. 1 is a plan view of a power tool when a working accessory is installed in a first embodiment of the present invention
  • FIG. 2 is a cross-sectional view of the power tool in FIG. 1 when a working accessory is installed;
  • FIG. 3 is an enlarged view of a part of the structure in FIG. 2;
  • FIG. 4 is a perspective view of the power tool in FIG. 1 when the left case is removed;
  • FIG. 5 is an exploded view of the power tool in FIG. 1 after the battery pack is removed;
  • FIG. 6 is a plan view of a vibrating body in the power tool in FIG. 1.
  • the power tool 100 may be an electric tool using electric energy as an energy source.
  • the power tool 100 may be a hand-held power tool. More specifically, the power tool 100 may For swinging tools.
  • the power tool 100 may be a swing type tool, and the swing type tool may be installed with different working accessories 200 such as triangular sand, shovel, metal saw blade, woodworking saw blade, emery Saw blades and the like, through these different working attachments 200, the power tool 100 can realize the functions of sawing, sanding, filing, shovel cutting and the like.
  • the power tool 100 can also be other power tools that generate relatively large vibrations during the work process, such as electric drills, electric hammers, reciprocating saws, sanders, etc., of course, as an optional implementation
  • the power tool 100 of this embodiment includes a main body and a working head provided at the front end.
  • the main source of vibration is generated by the working head, and the user is holding the main body. Therefore, such a power tool 100 uses the following disclosed herein. The substance will produce better vibration reduction effects.
  • the power tool 100 is a hand-held power tool.
  • the power tool 100 is a hand-held swing-type tool.
  • the power tool 100 includes a housing component 11, a power component 12, a transmission component, an output component 14, a clamping device 15, and an energy source.
  • the housing assembly 11 forms the outer shape of the power tool 100.
  • the power assembly 12 includes a prime mover configured to provide a driving force, and the prime mover is disposed inside the housing assembly 11.
  • the transmission component is an eccentric transmission component 13 capable of providing an oscillating motion.
  • the clamping device 15 is configured to mount the work attachment 200 to the power tool 100, and the clamping device 15 can also be considered as a part of the output assembly 14.
  • the energy source is the battery pack 16 in this embodiment. In other embodiments, the energy source may also be a power line provided with external AC power. Therefore, in this embodiment, the power tool 100 is an electric tool.
  • the housing assembly 11 includes a first housing 111 and a second housing 112.
  • the first housing 111 is at least partially disposed in the second housing 112, and the second housing 112 is formed with a handle portion 112a for holding by a user. .
  • the second casing 112 extends at least partially along the direction of the first straight line 101.
  • the first housing 111 is formed with a receiving cavity 111 a provided to receive and support the power assembly 12, the eccentric transmission assembly 13, and the output assembly 14.
  • the first casing 111 further specifically includes a head casing 111b and a power casing 111c, wherein the head casing 111b is configured to at least partially cover the output component 14 and the power casing 111c is configured to at least partially cover the power component 12 .
  • the part of the housing assembly 11 provided in the second housing 112 can also be considered as the first housing 111, and at least one between the first housing 111 and the second housing 112 is perpendicular to the first housing 111.
  • a gap 112 b is formed in the direction of the line 101.
  • the second casing 112 may specifically include a left casing 112c and a right casing 112d, and the left casing 112c and the right casing 112d may be arranged substantially symmetrically about a mid-plane 102, so that the left casing 112c and the right casing 112d are arranged symmetrically.
  • the formed handle portion 112 a is also disposed substantially symmetrically with respect to the mid-plane 102, and the first housing 111 may also be substantially symmetrical with respect to the mid-plane 102.
  • the power component 12, the eccentric transmission component 13, the output component 14, and the clamping device 15 provided in the first housing 111 or the second housing 112 are also arranged substantially symmetrically with respect to the mid-plane 102.
  • the power component 12 includes a prime mover configured to provide power to the output component 14.
  • the prime mover may specifically be a motor 121.
  • the motor 121 includes a motor shaft 121a.
  • the motor 121 is at least partially disposed in the power housing 111c.
  • the motor shaft 121a may be Projecting out of the power casing 111c, the motor 121 can still be considered to be disposed in the power casing 111c, and the power casing 111c can also be considered to be a part of the motor 121. That is to say, the power casing 111c can be considered as a casing provided outside the motor 121 and configured to wrap the motor 121, and the power casing 111 can also be considered as a casing of the motor 121 itself. As shown in FIGS.
  • the power casing 111 c includes a motor casing portion 111 d and a wind guide portion 111 e.
  • a wind guide portion 111e is provided between the motor case portion 111d and the head case 111b, and the wind guide portion 111e connects the motor case portion 111d and the head case 111b, so that the motor
  • the first casing 111 is formed as a whole by the casing portion 111d, the air guiding portion 111e, and the head casing 111b.
  • any casing portion that can directly receive the vibration transmitted from the eccentric transmission assembly 13 can be considered as the first casing 111.
  • a housing 111; or the housing portion that receives the vibration transmitted by the output component may be considered as the first housing 111; or, the housing of the working head portion may also be considered as the first housing 111.
  • the casing that can receive the vibration source provided in the power tool 100 to generate vibration can be considered as the first casing 111.
  • the first casing 111 supports the vibration source and is in contact with the vibration source. At least part of the casing of the first casing 111 is considered to be the second casing 112.
  • the motor shaft 121a can rotate relative to the housing assembly 11 with the motor axis 103 as an axis.
  • the motor axis 103 and the first straight line 101 can be considered to be coincident with each other.
  • An eccentric portion 131 is formed or connected to the end of the motor shaft 121 a near the output component 14 in the extending direction.
  • the eccentric portion 131 can be considered as a part of the eccentric transmission component 13.
  • 104 and the motor axis 103 are parallel to each other, and the distance between the central axis 104 and the motor axis 103 can be an eccentricity. It can be understood that when the eccentricity is large, the vibration generated by the power tool 100 will also increase.
  • the eccentric transmission assembly 13 further includes a bearing 132 and a swing lever 133.
  • the output assembly 14 includes an output member configured to output power, and the output member is specifically an output shaft 141 that can swing about the output axis 105 as an axis.
  • the bearing 132 is mounted on the eccentric portion 131. When the eccentric portion 131 rotates with the motor shaft 121a, the bearing 132 will also rotate with the motor axis 103 as the axis driven by the eccentric portion 131. In this way, the bearing 132 is perpendicular to the midplane
  • the left-right direction of 102 has a partial motion of left-right reciprocating motion.
  • the swing lever 133 includes a mounting portion 133a and a swing claw 133b.
  • the mounting portion 133a is fixedly connected to the output shaft 141.
  • the number of swing claws 133b is two.
  • Two swing claws 133b are provided on the left and right sides of the bearing 132, and two swing claws 133b. It is also provided on the left and right sides of the center plane 102. In this way, when the bearing 132 reciprocates, the two swing claws 133b will be reciprocated in the left-right direction.
  • the mounting portion 133a and the output shaft 141 form a fixed connection. The entirety of the mounting portion 133a and the output shaft 141 can swing back and forth within a range of swing angles with the output axis 105 as the axis.
  • the lever 133 will swing around the output axis 105, so that the swing lever 133 drives the output shaft 141 to swing within a range of a swing angle.
  • the power component 12, the eccentric transmission component 13 and the output component 14 are sources of vibration of the power tool 100.
  • the power component 12, the eccentric transmission component 13, and the output component 14 are basically disposed in the first casing 111. Therefore, the vibration generated by the power component 12 will first be transmitted to the first casing 111, and the casing
  • the assembly 11 includes two independent first and second cases 111 and 112, and a gap 112b is provided between the second and second cases 112 and 111, so that the vibration transmitted to the first case 111 is transmitted.
  • the bearing 132 strikes the swing claw 133b reciprocatingly in the left-right direction, and the output shaft 141 also reciprocates in a plane perpendicular to the mid-plane 102, so it can be understood that, in this embodiment, the working process of the power tool 100
  • the exciting force direction F of the exciting force of the vibration generated by the intermediate vibration source is substantially along the direction perpendicular to the mid-plane 102.
  • the vibration generated during the swing of the swing lever 133 is very much compared with other drill-type and circular-saw-type tools.
  • the first housing 111 and the second housing 112 are not provided with a very good vibration damping effect only by setting intervals.
  • the emergence of low-vibration power tools 100 is required to meet the user's requirements for low-vibration products, and on the other hand, the emergence of high-efficiency power tools 100 is also required.
  • the increase in efficiency will inevitably increase the vibration of the power tool 100.
  • a vibration reduction system 17 based on the structure of the above-mentioned case assembly 11 by the first case 111 and the second case 112 is also proposed.
  • the first casing 111 and the second casing 112 form a detachable connection, and the motor 121 may also be at least partially disposed in the second casing.
  • the vibration damping system 17 herein is also applicable to other power tools having only one housing.
  • the eccentricity can be eccentric
  • the entirety of the portion 131, the bearing 132, and the swing claw 133b is considered to be a vibration source 134.
  • the power module 12 connected to the eccentric portion 131, the output module 14 fixedly connected to the swing claw 133b, and the clamping device connected to the output module 14. 15 and the first housing 111 provided to install the motor 121, the eccentric transmission assembly 13, the output assembly 14, and the clamping device 15 all directly receive the vibration generated by the vibration source 134 through a solid structure connection.
  • the component that the source 134 is fixedly connected through the solid structure and directly receives the vibration generated by the vibration source 134 can be considered as the vibration body 10.
  • the vibration body 10 in addition to the eccentric transmission assembly 13 that generates the main vibration, the work attachment 200 that swings back and forth and processes the workpiece, the output assembly 14 and the clamping device 15 that rotate around the output axis 105, and a high-speed rotation Structures such as the motor 121 that also generate vibration but are not the main source of vibration are considered to be vibration bodies.
  • all the vibration sources 134 that generate vibration in the power tool 100 can be regarded as the vibration body 10, and the vibration sources 134 that generate large vibration in the power tool 100 can be regarded as the vibration body 10, and the vibration source 134 is The structure that is fixedly connected through the solid structure and directly receives the vibration generated by the vibration source 134 can also be selectively considered as a part of the vibration body 10 according to the specific situation.
  • a gap 112b is provided between the second casing 112 and the first casing 111, and is not directly connected or closely contacted with the vibration body 10 through a solid structure. Therefore, the second casing 112 may be considered as a non-vibration body 20
  • the battery pack 16 connected to the second case 112 should also be considered as the non-vibrating body 20. It can be understood that the screws, buckles, or other positioning structures and connection structures between the first casing 111 and the second casing 112 can be ignored, and these are not considered as the main solid structures for transmitting vibration.
  • a vibration reduction system 17 is provided between the vibrating body 10 and the non-vibrating body 20, thereby acting as a vibration isolation.
  • the power tool 100 may be installed with different work accessories 200 during use, and the weight, size and specifications of the work accessory 200 are changed when the structure of the power tool 100 is involved, Therefore, the work attachment 200 can be regarded as not part of the vibration body 10.
  • the influence of the work attachment 200 on the vibration body 10 can be ignored, and the movement direction of the work attachment 200 when it swings with the output shaft 141 is consistent with the output shaft 141.
  • the work attachment 200 can be regarded as not It belongs to a part of the vibration body 10, so that the user can set the structure and position of the vibration reduction system 17 and the like.
  • the size of the work attachment 200 is large, and it is not desirable to make the position and structure of the vibration damping system 17 an uncertain factor because of the size of the work attachment 200. Therefore, from this aspect, the main body of the vibration is included. 10 can also be considered as not including work attachment 200. That is to say, the power tool 100 herein can be regarded as a bare metal state when the work accessory 200 is not installed, so when the vibration main body 10 is identified, the power tool 100 in a bare metal state may prevail.
  • the vibration body 10 may include: a power component 12, an eccentric transmission component 13, an output component 14, a clamping device 15, and a first housing 111.
  • the vibration body 10 may also be considered as a driving body provided to drive the work accessory 200 and cause the work accessory 200 to implement a tool function.
  • the power tool 100 may be installed with different work attachments 200 during use, and when the size of the power tool 100 is involved, the size and specifications of the work attachment 200 are changed Therefore, it can be considered that the work attachment 200 does not belong to the vibration body 10.
  • the vibration damping system 17 is designed in consideration of the existence of the working attachment 200, in order to allow the public to clearly implement this article with the exclusion of some uncertain factors, the following dimensions and structures can be considered as power tools 100 is measured without work accessory 200 installed.
  • the vibration reduction system 17 is at least partially disposed between the first casing 111 and the second casing 112.
  • the first casing 111 serves as a supporting structure for the internal parts of the vibration body 10.
  • the vibration reduction of the vibration reduction system 17 can reduce transmission
  • the support structure to the non-vibrating body 20 is the vibration of the second casing 112. In this way, when the user holds the handle portion 112 a formed by the second housing 112, the user's hand can feel that the vibration generated by the power tool 100 is relatively weak, so that the user can hold the power tool 100 more stably to improve the power tool 100.
  • the machining effect on the workpiece can also make the user not feel fatigue after using the power tool 100 for a long time.
  • the eccentric portion 131 drives the bearing 132 to strike the swing claw 133b in the left-right direction, and the output shaft 141 also basically swings in the left-right direction. Therefore, the eccentric transmission component 13 can be understood as a vibration source, and the output component 14 also It can be understood as a vibration source, or the whole formed by them can be understood as a vibration source. Therefore, in this embodiment, the direction F of the excitation force of the vibration generated by the vibration source and the motor axis 103 are perpendicular to each other. Therefore, in this embodiment, the excitation force direction F of the vibration generated by the vibration source can also be considered as the excitation force direction F of the vibration generated by the vibration body 10. The direction of excitation force F of the vibration generated by the vibration body 10 described below can be understood as the direction of excitation force F of the vibration generated by the vibration source.
  • the exciting force direction F of the exciting force generated by the vibrating body 10 and the mid-partition plane 102 are perpendicular to each other, so the vibration damping system 17 can be set in a direction F that is parallel to the exciting force.
  • vibration isolation is performed in a plane perpendicular to the mid-partition plane 102, so that the vibration transmitted from the vibration body 10 to the non-vibration body 20 along the excitation force direction F of the excitation force can be effectively reduced.
  • the vibration damping system 17 is disposed at least partially between the first casing 111 and the second casing 112 in the direction F of the exciting force, or the vibration damping system 17 separates the first casing 111 and the second casing 111 At least a portion of the housing 112 is spaced apart in the direction F of the excitation force.
  • the vibration body 10 is provided with at least two first and second planes perpendicular to the motor axis 103 of the motor shaft 121a, and the vibration damping system 17 includes: at least one first spacer disposed on the first plane The vibration block 173 and at least one second vibration isolation block 174 disposed on the second plane.
  • the first plane may be defined as a first vibration isolation plane 171 and the second plane may be defined as a second vibration isolation plane 172.
  • the entirety of the first vibration isolating block 173 and the second vibration isolating block 174 has at least a space portion 17 a provided between the first casing 111 and the second casing 112, and the second casing 112
  • the space is separated from the first case 111 at the space portion 17a, and the first vibration isolation block 173 and the second vibration isolation block 174 are also separated from each other.
  • the first vibration isolation block 173 is disposed between the first casing 111 and the second casing 112
  • the second vibration isolation block 174 is disposed between the first casing 111 and the second casing 112.
  • the second casing 112 is spaced from the first casing 111 at the first vibration isolation block 173, and the second casing 112 is also spaced from the first casing 111 at the second vibration isolation block 174.
  • the separation of the first vibration isolation block 173 and the second vibration isolation block 174 from each other can be understood as the first vibration isolation block 173 and the second vibration isolation block 174 are not integrally formed, and they are separated by a certain distance. In this way, by providing the first vibration isolation block 173 and the second vibration isolation block 174 spaced apart in the power tool 100, the vibration reduction effect of the vibration reduction system 17 can be improved, thereby improving the work efficiency of the user.
  • the first vibration isolation block 173 and the second vibration isolation block 174 are spaced apart from each other in a direction perpendicular to the first vibration isolation plane 171.
  • the first vibration isolation plane 171 and the second vibration isolation plane 172 are also perpendicular to the mid-part plane 102 of the vibration body 10.
  • the first vibration isolation plane 171 and the second vibration isolation plane 172 are also related to the excitation force generated by the vibration body 10.
  • the excitation force directions F are parallel to each other.
  • the first vibration isolation plane 171 and the second vibration isolation plane 172 are also mutually flat with the output axis 105 of the output shaft 141.
  • the output shaft 141 swings in a plane perpendicular to the output axis 105.
  • the first vibration isolation plane 171 and the second vibration isolation plane 172 are also perpendicular to the plane where the output shaft 141 swings, and the first vibration isolation plane 171 and the second vibration isolation plane 172 are also perpendicular to the first straight line 101.
  • the first vibration isolation block 173 on the first vibration isolation plane 171 and the second vibration isolation block 174 on the second vibration isolation plane 172 can reduce the vibration transmitted from the vibration body 10 to the non-vibration body 20.
  • the direction along the first straight line 101 and the direction from the first vibration isolation plane 171 toward the second vibration isolation plane 172 is also defined as the direction along the first straight line 101 and from the second vibration isolation plane 172.
  • the direction toward the first vibration isolation plane 171 is forward.
  • the vibration damping system 17 can reduce the vibration transmitted by the vibrating body 10 to the non-vibrating body 20 along the exciting force direction F. Therefore, we can also set it like this, first define a partition plane perpendicular to the exciting force direction F
  • the vibration body 10 is provided with at least two first vibration isolation planes 172 and a second vibration isolation plane 172 that are perpendicular to the isolation plane, and the first vibration isolation planes 171 and the first vibration isolation blocks on the second vibration isolation plane 172.
  • the second vibration isolating block 174 can separate the path of vibration transmission in the direction of the exciting force direction F and the direction that obliquely intersects the exciting force direction F, so as to absorb the vibration generated by the vibration body 10 and further reduce The vibration of the small-vibration body 10 is transmitted to the non-vibration body 20 in the excitation force direction F.
  • the length of the vibration body 10 in the direction along the motor axis 103 is L, that is, the length of the vibration body 10 in the direction in which the handle portion 112 a extends is L, or It is said that the length of the vibration body 10 in the direction perpendicular to the first vibration isolation plane 171 is L.
  • the length L can also be understood Is the length of the first casing 111.
  • the vibration body 10 also has a center of gravity G.
  • the distance between the first vibration isolation plane 171 and the center of gravity G is L1, that is, the first vibration isolation plane 171 and The distance between the center of gravity G in the direction of the motor axis 103 is L1, or the size of the first vibration isolation plane 171 and the center of gravity G in a direction perpendicular to the first vibration isolation plane 171 is L1.
  • the ratio of the distance L1 between the first vibration isolation plane 171 and the center of gravity G in the direction of the motor axis 103 to the length L of the vibration body 10 in the direction of the motor axis 103 is greater than or equal to 0 and less than or equal to 0.3, that is, That is, the distance L1 between the first vibration isolation plane 171 and the center of gravity G in a direction perpendicular to the first vibration isolation plane 171 and the length L of the vibration body 10 in a direction perpendicular to the first vibration isolation plane 171
  • the ratio of is greater than or equal to 0 and less than or equal to 0.3.
  • the ratio of the distance L1 between the first vibration isolation plane 171 and the center of gravity G in the direction of the motor axis 103 to the length L of the vibration body 10 in the direction of the motor axis 103 is greater than or equal to 0 and less than or equal to 0.3, which refers to the first vibration isolation.
  • the plane 171 passes through the center of gravity G or is provided on the front side or the rear side of the center of gravity at a distance of 0.3 L from the center of gravity G.
  • the distance between the first vibration isolation plane 171 and the second vibration isolation plane 172 is L2, that is, the distance between the first vibration isolation plane 171 and the second vibration isolation plane 172 is along the motor.
  • the distance in the direction of the axis 103 is L2, or in other words, the distance between the first vibration isolation plane 171 and the second vibration isolation plane 172 in a direction perpendicular to the first vibration isolation plane 171 is L2.
  • the ratio of the distance L2 between the first vibration isolation plane 171 and the second vibration isolation plane 172 in the direction of the motor axis 103 to the length L of the vibration body 10 in the direction of the motor axis 103 is greater than or equal to 0.3 and less than or equal to 0.7, that is, That is, the distance L2 between the first vibration isolation plane 171 and the second vibration isolation plane 172 in a direction perpendicular to the first vibration isolation plane 171 and the vibration main body 10 in a direction perpendicular to the first vibration isolation plane 171
  • the ratio between the lengths L is 0.3 or more and 0.7 or less.
  • the position of the second vibration isolation plane 172 is reasonable.
  • the vibration reduction effect of the vibration reduction system 17 can be improved, and on the other hand, the first casing 111 and the second casing 112 can be more stably supported.
  • the first vibration isolation plane 171 is located on the front side of the center of gravity G, and the distance L1 between the first vibration isolation plane 171 and the center of gravity G in the direction of the motor axis 103 and the distance of the vibration main body 10 in the direction of the motor axis 103
  • the ratio of the length L is greater than or equal to 0.2 and less than or equal to 0.3, wherein “between” in this embodiment includes the end point position; or the first vibration isolation plane 171 is located on the front side of the center of gravity G, and the first vibration isolation plane 171 and
  • the ratio of the distance L1 between the center of gravity G in the direction of the motor axis 103 and the length L of the vibration body 10 in the direction of the motor axis 103 is greater than or equal to 0.1 and less than or equal to 0.2, thereby improving the vibration reduction effect of the vibration reduction system 17;
  • the vibration isolation plane 171 is located in front of the center of gravity G, and the ratio of the distance L1 between the first vibration isolation plane 171 and the center
  • the ratio between the distance L1 in the direction of the motor axis 103 between the first vibration isolation plane 171 and the center of gravity G and the length L of the vibration body 10 in the direction of the motor axis 103 is greater than or equal to 0 and less than or equal to 0.05, that is, That is, the first vibration isolation plane 171 is located between 0.05L on the front side of the center of gravity G and 0.05L on the rear side, so that the first vibration isolation plane 171 is closer to the center of gravity G, thereby improving the vibration reduction effect of the vibration reduction system 17;
  • the first vibration isolation plane 171 is located on the rear side of the center of gravity G, and the ratio of the distance L1 between the first vibration isolation plane 171 and the center of gravity G in the direction of the motor axis 103 to the length L of the vibration body 10 in the direction of the motor axis 103 is greater than Equal to 0 and less than or equal to 0.1, thereby increasing Damping effect of the system 17; or, the first vibration isolation plane 171 is located on
  • the ratio of the distance L2 between the first vibration isolation plane 171 and the second vibration isolation plane 172 in the direction along the motor axis 103 to the length L of the vibration body 10 in the direction along the motor axis 103 is greater than or equal to 0.3 and less than or equal to 0.4; or The ratio of the distance L2 between the first vibration isolation plane 171 and the second vibration isolation plane 172 in the direction along the motor axis 103 to the length L of the vibration body 10 in the direction along the motor axis 103 is greater than or equal to 0.4 and less than or equal to 0.5; or The ratio of the distance L2 between the first vibration isolation plane 171 and the second vibration isolation plane 172 in the direction along the motor axis 103 to the length L of the vibration body 10 in the direction along the motor axis 103 is greater than or equal to 0.5 and less than or equal to 0.7.
  • any one of the ranges of the ratio between the distance L1 in the direction of the motor axis 103 between the first vibration isolation plane 171 and the center of gravity G and the length L of the vibration body 10 in the direction of the motor axis 103 can be equal to
  • the combination of any one of the ratios of the distance L2 between the first vibration isolation plane 171 and the second vibration isolation plane 172 in the direction along the motor axis 103 and the length L of the vibration body 10 in the direction along the motor axis 103 is combined. Any combination of can make the damping system 17 achieve a good damping effect.
  • first vibration isolation plane 171 is disposed on the front side of the center of gravity G
  • second vibration isolation plane 172 is disposed on the rear side of the center of gravity G, that is, the center of gravity G is disposed on the first vibration isolation plane 171 and
  • the second vibration isolation plane 172 can further improve the vibration reduction effect; and the difference in the distance between the first vibration isolation plane 171 and the second vibration isolation plane 172 also affects the vibration reduction effect.
  • the distance between the first vibration isolation plane 171 and the second vibration isolation plane 172 is set within a reasonable range, so that the vibration reduction effect of the power tool 100 is optimal.
  • the distance between the center of gravity G and the vibration source 134 is greater than or equal to 0 and less than or equal to 0.2L, that is, the center of gravity G is as close to the motor axis 103 as possible.
  • the vibration source 134 so that when the first vibration isolation plane 171 is set close to the center of gravity G, the main vibration amount generated by the vibration body 10 can be isolated, and the second vibration isolation plane 172 can be provided to further isolate other vibrations of the vibration body 10 The amount of vibration can further improve the vibration reduction effect of the vibration reduction system 17.
  • first vibration isolation blocks 173 are disposed on the first vibration isolation plane 171, and the first vibration isolation blocks 173 are disposed on the head casing 111b, that is, two head vibration isolation blocks 171 are disposed on the first casing 111b.
  • the first vibration isolation blocks 173 are also disposed on both sides of the mid-plane 102 respectively.
  • the first vibration isolation block 173 has a forward stiffness having a size K, and the direction of the forward stiffness of the first vibration isolation block 173 is D.
  • the angle between the direction D of the forward stiffness of the first vibration isolation block 173 and the direction F of the excitation force is greater than or equal to 0 degrees and less than or equal to 60 degrees.
  • the first vibration isolation The angle between the direction D of the forward stiffness of the block 173 and the direction F of the exciting force is greater than or equal to 0 degrees and less than or equal to 45 degrees.
  • the positive stiffness of the first vibration isolation block 173 is The angle between the direction D and the direction F of the excitation force is greater than or equal to 0 degrees and less than or equal to 30 degrees.
  • the direction D of the forward stiffness of the first vibration isolation block 173 and the excitation The included angle between the directions of the exciting force F of the force is greater than or equal to 0 degrees and less than or equal to 10 degrees.
  • the direction D and the exciting force of the forward stiffness of the at least one first vibration isolation block 173 may also be made.
  • the direction of the exciting force F is parallel.
  • at least one first vibration isolation block 173 may be disposed on an orthographic projection of the excitation force direction F on the first vibration isolation plane 171. In this way, the direction D of the forward rigidity of the first vibration isolation block 173 can be made as close as possible to the excitation force direction F of the excitation force, so that the vibration reduction effect of the vibration reduction system 17 can be better improved.
  • the included angle between the direction D of the forward stiffness of the first vibration isolation block 173 and the direction F of the excitation force is greater than or equal to 0 degrees and less than or equal to 15 degrees; or the forward stiffness of the first vibration isolation block 173
  • the included angle between the direction D of the excitation force and the direction F of the excitation force is 15 degrees or more and 30 degrees or less; or, the direction D of the forward stiffness of the first vibration isolation block 173 and the excitation of the excitation force
  • the angle between the force directions F is 30 degrees or more and 45 degrees or less; or, the angle between the direction D of the forward stiffness of the first vibration isolation block 173 and the direction F of the excitation force is greater than or equal to 45 degrees and 60 degrees or less.
  • the first vibration isolation block 173 is disposed in a plane perpendicular to the mid-plane 102 and passing through the motor axis 103, that is, the first vibration isolation
  • the direction D of the forward stiffness of the block 173 and the left-right direction of the movement of the eccentric portion 131 are parallel to each other. In this way, the vibration reduction effect of the vibration reduction system 17 can be better improved.
  • the number of the second vibration isolation blocks 174 on the second vibration isolation plane 172 is at least two or more.
  • the orthographic projections of the plurality of first vibration isolation blocks 173 on the first vibration isolation plane 171 in a plane perpendicular to the motor axis 103 and the plurality of second vibration isolation blocks 174 on the second vibration isolation plane 172 are perpendicular to the motor axis
  • the orthographic projections in the plane of 103 are at least partially staggered, the orthographic projections of the plurality of first vibration isolation blocks 173 on the first vibration isolation plane 171 on the plane perpendicular to the motor axis 103 and the second vibration isolation plane 172
  • the orthographic projections of the plurality of second vibration isolation blocks 174 in a plane perpendicular to the motor axis 103 may also be completely staggered, and the plane is also parallel to the first vibration isolation plane 171.
  • the orthographic projection of 174 in a plane perpendicular to the motor axis 103 is at least partially staggered in a circumferential direction around the motor axis 103.
  • the orthographic projections of the plurality of first vibration isolation blocks 173 on the first vibration isolation plane 171 in a plane perpendicular to the motor axis 103 are a plurality of first projections
  • the plurality of second projections on the second vibration isolation plane 172 are
  • the orthographic projection of the vibration isolation block 174 in a plane perpendicular to the motor axis 103 is a plurality of second projections, wherein at least part of the plurality of first projections and at least part of the plurality of second projections are in The circumferential direction is staggered in order.
  • the orthographic projections of the plurality of first vibration isolation blocks 173 on the first vibration isolation plane 171 in a plane perpendicular to the motor axis 103 and the plurality of second vibration isolation blocks on the second vibration isolation plane 172 are sequentially staggered in the circumferential direction around the motor axis 103.
  • the second vibration isolation on the second vibration isolation plane 172 can absorb the vibration of the vibration body 10 in directions other than the excitation force direction F of the excitation force as much as possible, so as to better improve the vibration reduction effect of the vibration reduction system 17.
  • the second vibration isolation block 174 is mounted on the housing of the motor 121.
  • both the impact direction of the eccentric portion 131 on the swing lever 133 and the swing direction of the output shaft 141 are substantially parallel to the direction F of the exciting force, and the The impact direction and the swing direction of the output shaft 141 are substantially perpendicular to the motor axis 103. Therefore, setting the first vibration isolation block 173 and the second vibration isolation block 174 in a plane perpendicular to the motor axis 103 can effectively reduce eccentricity.
  • the primary vibration generated by the impact of the portion 131 on the swing lever 133 can also reduce the secondary vibration generated by the swing of the output shaft 141.
  • the number of the first vibration isolation blocks 173 is two or more.
  • the first vibration isolation blocks 173 are sequentially arranged in a circumferential direction around the motor axis 103, and in the circumferential direction, two adjacent vibration isolation blocks 173 are arranged in sequence. There is also a gap between the first vibration isolation blocks 173, that is, any two first vibration isolation blocks 173 are spaced apart; the number of the second vibration isolation blocks 174 is two or more,
  • the second vibration isolation blocks 174 are sequentially arranged in a circumferential direction around the motor axis 103, and in the circumferential direction, there is a gap between two adjacent second vibration isolation blocks 174, that is, any two first vibration isolation blocks 174
  • the two vibration isolation blocks 174 are spaced apart. In this way, the vibration generated by the vibration body 10 can be isolated from multiple directions, and the vibration reduction effect can be improved.
  • the first vibration isolation plane 171 uses a plurality of first vibration isolation blocks 173 disposed at intervals to achieve a vibration reduction effect. It can be understood that in other embodiments, the first vibration isolation Vibration isolation may also be achieved on the plane 171 by providing a ring-shaped vibration isolation block extending in a circumferential direction around the motor axis 103. Similarly, the second vibration isolation plane 172 can achieve vibration reduction effects through a plurality of second vibration isolation blocks 174 disposed at intervals. It can be understood that in other embodiments, the second vibration isolation plane 172 can also be provided by A ring-shaped vibration isolation block extending in a circumferential direction around the motor axis 103 is used to achieve vibration isolation.
  • the first vibration isolation plane 171 and the second vibration isolation plane 172 are spaced apart, that is, the first vibration isolation block 173 and the second vibration isolation block 174 are perpendicular to the first vibration isolation plane along the The directions of 171 are spaced apart, so that on the one hand, the vibration isolation effect can be improved while using as few vibration isolation blocks as possible, and on the other hand, the first housing 111 is located on the first vibration isolation plane 171 and the second vibration isolation.
  • a gap is provided between a portion between the planes 172 and a portion of the second casing 112 located between the first vibration isolation plane 171 and the second vibration isolation plane 172, thereby further preventing the first casing 111 from being transmitted to the second Vibration of the housing 112.
  • a portion of the first housing 111 between the first and second vibration isolation planes 171 and 172 and a portion of the second housing 112 between the first and second vibration isolation planes 171 and 172 The gap provided between the sections 172 is an annular gap around the motor axis 103.
  • the second vibration isolation block 174 on the second vibration isolation plane 172 is disposed on the motor housing portion 111d, that is, the second vibration isolation plane 172 passes through the motor housing portion 111d.
  • the vibration body 10 further includes a third vibration isolation plane 175 that is perpendicular to the motor axis 103 of the motor shaft 121a.
  • a third vibration isolation block and a third vibration isolation plane are provided on the third vibration isolation plane 175. 175 is also disposed between the first vibration isolation plane 171 and the second vibration isolation plane 172.
  • the first vibration isolation block 173, the second vibration isolation block 174, and the third vibration isolation block are all made of polyurethane foam material, which has good elasticity and good recovery performance.
  • the first vibration isolation block 173 or the second vibration isolation block 174 is also disposed in the handle portion 112a, so that the vibration transmitted to the user's hand can be further reduced.
  • the maximum rotation speed of the motor 121 is R revolutions per minute
  • the swing angle of the output shaft 141 is A degrees, where the ratio of the rotation speed R of the motor 121 to the vibration acceleration a of the power tool 100 5000 or more and 20000 or less.
  • the ratio of the swing angle A of the output shaft 141 to the vibration acceleration a of the power tool 100 is 1 or more and 3 or less.
  • the ratio of the speed R of the motor 121 to the vibration acceleration a of the power tool 100 is greater than or equal to 5000 and less than or equal to 6000, or the ratio of the speed R of the motor 121 to the vibration acceleration a of the power tool 100 is greater than or equal to 6000 and 10,000 or less, or a ratio of the rotation speed R of the motor 121 to the vibration acceleration a of the power tool 100 is 10,000 or more and 20,000 or less.
  • the ratio of the swing angle A of the output shaft 141 to the vibration acceleration a of the power tool 100 is 1 or more and 1.7 or less; or the ratio of the swing angle A of the output shaft 141 to the vibration acceleration a of the power tool 100 is 1.7 or more and less than 3.
  • the rotation speed R of the motor 121 can be 20,000 or more and 22,000 or less, or the rotation speed R of the motor 121 can be made greater than or equal to 22000, the swing angle A of the output shaft 141 may be 3.6 or more and 5 or less, or the swing angle A of the output shaft 141 may be 5 or more.

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Abstract

一种动力工具（100），包括：动力组件（12），其包括电机（121），电机（121）包括绕电机轴线转动的电机轴（121a）；输出组件（14），其包括输出轴（141）；传动组件（13）；第一壳体（111）；第二壳体（112）；动力工具（100）设置有第一隔振平面（171）和第二隔振平面（172），第一隔振平面（171）上设置有第一隔振块（173），第二隔振平面（172）设置有第二隔振块（174）；第一隔振块（173）和第二隔振块（174）构成的整体中至少具有设置于第一壳体（111）和第二壳体（112）之间的间隔部分（17a），第二壳体（112）在间隔部分（17a）处与第一壳体（111）间隔开；第一隔振块（173）和第二隔振块（174）相互分离。

Description

动力工具
本公开要求在2018年06月05日提交中国专利局、申请号为201810566644.5，在2018年11月29日提交中国专利局、申请号为201811442212.X的中国专利申请的优先权，以上申请的全部内容通过引用结合在本公开中。
技术领域
本文涉及一种动力工具，例如涉及一种摆动类工具。
背景技术
诸如电锤、往复锯、摆动类工具等的动力工具在工作过程中会产生振动，这样会影响被加工的工件的加工效果，而这一类的手持式动力工具在用户握持它们进行工作时，工具本身所产生的振动会通过人手传递至用户，从而使得用户无法稳定的握持工具，而且还会使得用户在工作一段时间后就感觉到疲劳。特别是对于摆动类工具而言，其包括用于实现摆动的偏心传动组件，这样摆动类工具在开机后具有很大的振动，一方面这使得用户无法稳定的握持摆动类工具，从而影响被锯切的工件的加工效果，另一方面用户在使用一段时间后会感到非常疲劳，从而影响工作效率。
发明内容
为解决现有技术的不足，本文提供了一种减振效果好的动力工具。
本文采用如下的技术方案：
一种动力工具，包括：动力组件，包括电机，电机包括能绕电机轴线转动的电机轴；输出组件，包括设置为输出动力的输出轴；传动组件，设置为在动力组件和输出组件之间实现动力的传递；第一壳体，至少能支撑动力组件、传动组件和输出组件；第二壳体，对第一壳体至少部分进行包围，第二壳体还形成有设置为供用户握持的把手部；其中，动力工具设置有第一隔振平面和第二隔振平面，第一隔振平面上设置有第一隔振块，第二隔振平面设置有第二隔振块；第一隔振块和第二隔振块构成的整体中至少具有设置于第一壳体和第二壳体之间的间隔部分，第二壳体在间隔部分处与第一壳体间隔开；第一隔振块和第二隔振块相互分离。
附图说明
图1是本文第一实施例的动力工具安装工作附件时的平面图；
图2是图1中的动力工具安装工作附件时的剖视图；
图3是图2中部分结构的放大图；
图4是图1中的动力工具在去除左壳体时的立体图；
图5是图1中的动力工具在去除电池包后的***图；
图6是图1中的动力工具中的振动主体的平面图。
具体实施方式
如图1所示，本文提出一种动力工具100，该动力工具100可以为采用电能作为能量来源的电动工具，该动力工具100可以为手持式动力工具，更具体而言，该动力工具100可以为摆动类工具。如图1所示，在具体实施例中，动力工具100可选为摆动类工具，该摆动类工具可安装不同的工作附件200，例如三角砂、铲刀、金属锯片、木工锯片、金刚砂锯片等，通过这些不同的工作附件200能够使得动力工具100实现锯切、砂磨、锉磨以及铲切等的功能。当然可以理解的，该动力工具100还可以为其它在工作过程中会产生比较大的振动的动力工具，例如还可以是电钻、电锤、往复锯、砂光机等，当然作为可选的实施例，本实施例的动力工具100包括主体以及设置在前端的工作头，主要的振动来源由工作头所产生，而用户是握持在主体上的，因此这样的动力工具100采用本文以下披露的实质内容将会产生更好的减振效果。
以下具体介绍该动力工具100的具体结构以及工作原理。
参照图1和图2所示，动力工具100为手持式的动力工具，在本实施例中，动力工具100为手持式的摆动类工具。具体而言，动力工具100包括：壳体组件11、动力组件12、传动组件、输出组件14、夹持装置15以及能量源。其中，壳体组件11形成了动力工具100的外形，动力组件12包括设置为提供驱动力的原动机，原动机设置在壳体组件11内部。在本实施例中，对于摆动类工具而言，传动组件为能提供振荡运动的偏心传动组件13。夹持装置15设置为将工作附件200安装至动力工具100，夹持装置15也可以认为是属于输出组件14的一部分。能量源在本实施例中为电池包16，在其它实施例中，能量源也可以为设置为外接交流电的电源线，因此，在本实施例中，动力工具100以电动工具为例。
壳体组件11包括：第一壳体111和第二壳体112，第一壳体111至少部分设置在第二壳体112内，第二壳体112形成有用于供用户握持的把手部112a。第二壳体112至少部分沿第一直线101方向延伸。第一壳体111形成有设置为容纳并支撑动力组件12、偏心传动组件13以及输出组件14的容纳腔111a。第一壳体111具体还包括：头壳111b和动力壳体111c，其中，头壳111b设置为对输出组件14进行至少部分包覆，动力壳体111c设置为对动力组件12进行至少部分包覆。事实上，也可以将壳体组件11中设置在第二壳体112内的部分认为是第一壳体111，第一壳体111和第二壳体112之间至少在一个垂直于第一直线101的方向上形成有间隙112b。第二壳体112具体可以包括左壳体112c和右壳体112d，左壳体112c和右壳体112d可以基本关于一个中分面102对称设置，这样由左壳体112c和右壳体112d所形成的把手部112a也基本关于中分面102对称设置，而第一壳体111也可以关于中分面102基本对称。设置在第一壳体111或者第二壳体112内的动力组件12、偏心传动组件13、输出组件14以及夹持装置15也基本关于中分面102对称设置。
动力组件12包括：设置为给输出组件14提供动力的原动机，该原动机具体可以为电机121，电机121包括电机轴121a，电机121至少部分设置在动力壳体111c内，其中电机轴121a可能伸出至动力壳体111c外，这时依然可以认为电机121设置在动力壳体111c内，动力壳体111c也可以认为是属于电机121的一部分。也即是说，动力壳体111c可以认为是设置在电机121外设置为对电机121进行包裹的壳体，动力壳体111也可以被认为是电机121自身的外壳。如图2至图5所示，在一些实施例中，动力壳体111c包括：电机壳体部111d和导风部111e。在沿第一直线101方向上，导风部111e设置在电机壳体部111d和头壳111b之间，导风部111e连接了电机壳体部111d和头壳111b，从而使得电机壳体部111d、导风部111e以及头壳111b构成的整体组成了第一壳体111，事实上，只要是能够直接接收到偏心传动组件13传递过来的振动的壳体部分均可以认为是第一壳体111；或者，也可以将接收到输出组件传递过来的振动的壳体部分认为是第一壳体111；再或者，还可以将工作头部分的壳体认为是第一壳体111。总结来说，就是能够接收到动力工具100中设置为产生振动的振动源的壳体可以认为是第一壳体111，第一壳体111对振动源构成支撑并与振动源接触，而包覆至少部分第一壳体111的壳体则认为是第二壳体112。
电机轴121a相对壳体组件11能以电机轴线103为轴转动，在本实施例中， 电机轴线103和第一直线101可以认为是相互重合的。电机轴121a在延伸方向上靠近输出组件14的一端形成或者连接有偏心部131，偏心部131可以被认为是偏心传动组件13的一部分，偏心部131具有一个中心轴线104，偏心部131的中心轴线104与电机轴线103相互平行，中心轴线104与电机轴线103之间的距离可以成为是偏心距，可以理解的，当偏心距较大时，动力工具100所产生的振动也会随之增大。偏心传动组件13还包括：轴承132和摆杆133，输出组件14包括：设置为输出动力的输出件，该输出件具体为能以输出轴线105为轴摆动的输出轴141。轴承132安装至偏心部131上，当偏心部131随着电机轴121a转动时，轴承132也会在偏心部131的驱动下以电机轴线103为轴转动，这样，轴承132在垂直于中分面102的左右方向上具有左右往复运动的分运动。摆杆133包括安装部133a和摆爪133b，安装部133a与输出轴141构成固定连接，摆爪133b的数目为2，两个摆爪133b设置在轴承132的左右两侧，两个摆爪133b也设置在中分面102的左右两侧。这样，当轴承132往复运动时，将会在左右方向上往复撞击两个摆爪133b。安装部133a与输出轴141构成固定连接，安装部133a和输出轴141构成的整体能以输出轴线105为轴在一个摆动角度范围内往复摆动，当两个摆爪133b被轴承132撞击时，摆杆133将会以输出轴线105为轴摆动，从而摆杆133带动输出轴141在一个摆动角度的范围内摆动。由此可见，动力组件12、偏心传动组件13以及输出组件14是动力工具100振动的来源。而本文中，动力组件12、偏心传动组件13以及输出组件14基本设置在第一壳体111内，因此，动力组件12所产生的振动首先将会传递至第一壳体111上，而壳体组件11包括两个独立的第一壳体111和第二壳体112，且第二壳体112与第一壳体111之间还具有间隙112b，这样，传递至第一壳体111上的振动将会被一定程度的衰减后才能传递至第二壳体112，而把手部112a由第二壳体112所形成，这样由第二壳体112传递至用户的手的振动也会被一定程度的削弱，从而提高整机的减震效果。其中，轴承132是沿左右方向往复的撞击摆爪133b的，输出轴141也是在垂直于中分面102的平面内往复运动的，因此可以理解的，在本实施例中，动力工具100工作过程中振动源所产生的振动的激振力的激振力方向F基本沿垂直于中分面102的方向。
事实上，在本文中，特别是对于本实施例中的摆动类工具而言，其在摆杆133摆动的过程中所产生的振动相较于其它的钻类、圆锯类工具而言是非常大的，而仅仅是通过设置间隔设置的第一壳体111和第二壳体112并不能达到非常好的 减振效果。换句话说，在市场日益增进的需求下，一方面需要低振动的动力工具100的出现，以满足用户对低振动的产品的要求，另一方面还需要高效率的动力工具100的出现。而对于动力工具100而言，效率的提高势必会使得动力工具100的振动增大，因此有必要对这一类的高切割效率的动力工具100设计出减振效果更好的减振结构。特别是对于本实施例中的摆动类工具而言，一方面我们希望通过增大摆动角度以提高切割效率，另一方面，当摆动角度增大时摆动类工具会振动的更厉害。因此，在本文中，还提出了一种基于上述的壳体组件11由第一壳体111和第二壳体112组成的结构的减振***17。其中，需要说明的是，第一壳体111和第二壳体112构成可拆卸连接，电机121也可以至少部分设置在第二壳体内。事实上，本文中的减振***17也适用于其它仅仅具有一个壳体的动力工具。
在本实施例中，特别是对于本实施例的摆动类工具而言，其振动主要是由偏心部131带动轴承132转动且转动的轴承132往复的撞击摆爪133b所产生的，因此可以将偏心部131、轴承132以及摆爪133b所构成的整体认为是振动源134，而与偏心部131连接的动力组件12、与摆爪133b固定连接的输出组件14、与输出组件14连接的夹持装置15以及设置为安装电机121、偏心传动组件13、输出组件14和夹持装置15的第一壳体111均通过实体结构固定连接的方式来直接接收振动源134所产生的振动，这样的与振动源134通过实体结构固定连接并直接接收到振动源134所产生的振动的组件可以被认为是振动主体10。或者，除了产生主要振动的偏心传动组件13之外，还可以将往复摆动且对工件进行加工的工作附件200、以输出轴线105为轴转动的输出组件14和夹持装置15、以及高速转动的电机121等这一类也产生振动但不是最主要的振动来源的结构均认为是振动主体。也即是说，可以将动力工具100中所有产生振动的振动源134认为是振动主体10，也可以将动力工具100中产生振动较大的振动源134认为是振动主体10，而与振动源134通过实体结构固定连接并直接接收振动源134产生的振动的结构根据具体情况也可以选择性的将其认为是振动主体10的一部分。而第二壳体112与第一壳体111之间设置有间隙112b，且没有直接与振动主体10通过实体结构固定连接或者紧密接触，因此，第二壳体112可以是被认为是非振动主体20，而与第二壳体112连接的电池包16也应当被认为是非振动主体20。可以理解的，对于第一壳体111与第二壳体112之间的螺钉、卡扣或者其它一些定位结构、连接结构可以忽略，认为这些不是用于传递振动的 主要的实体结构。
在本实施例中，为了减小振动主体10传递至非振动主体20的振动，在振动主体10和非振动主体20之间设置了减振***17，从而起到了隔振的作用。考虑到对于摆动类多功能工具而言，动力工具100在使用过程中可能会安装不同的工作附件200，且在涉及动力工具100的结构时，工作附件200的重量、尺寸以及规格是变化的，因此可以将工作附件200认为是不属于振动主体10的一部分。一方面，从重量上来说，工作附件200对振动主体10的影响可以忽略，且工作附件200随输出轴141摆动时的运动方向也与输出轴141一致，因此，可以将工作附件200认定为不属于振动主体10的一部分，从而方便用户设定减振***17的结构以及位置等。另一方面，工作附件200的尺寸较大，在设计时不希望因为工作附件200的尺寸影响而使得减振***17的位置以及结构变成一个不确定因素，因此从这一方面包括，振动主体10也可以认为是不包含工作附件200的。也即是说，本文中的动力工具100可以认为是未安装工作附件200时的裸机状态，因此在认定振动主体10时也可以仅仅以裸机状态的动力工具100为准。更具体而言，在本实施例中，振动主体10可以包括：动力组件12、偏心传动组件13、输出组件14、夹持装置15以及第一壳体111，而对于其它类型的动力工具100而言，振动主体10也可以认为是设置为驱动工作附件200并使得工作附件200实现工具功能的驱动主体。为了对方案进行介绍，且考虑到对于摆动类工具而言，动力工具100在使用过程中可能会安装不同的工作附件200，且在涉及动力工具100的尺寸时，工作附件200尺寸以及规格是变化的，因此可以认为工作附件200是不属于振动主体10的。但事实上，在设计人员设计时，因为工作附件200在工作过程中与工件直接接触，因此其所产生的振动将会比较大，因此在设计减振***17中的具体结构、位置以及参数时可以是考虑工作附件200的存在的。只是在考虑工作附件200存在的情况下将减振***17设计好之后，为了让公众能够在排除一些不确定因素的情况之下清楚的实现本文，可以认为以下所涉及的尺寸和结构是动力工具100在未安装工作附件200的情况下进行测量的。
减振***17至少部分设置在第一壳体111和第二壳体112之间，第一壳体111作为振动主体10内部零件的支撑结构，其通过减振***17的减振，可以降低传递至非振动主体20的支撑结构也即是第二壳体112的振动。这样，用户在握持由第二壳体112所形成的把手部112a时，用户的手能够感受到动力工具100 所产生的振动较弱，从而能够更稳定的握持动力工具100以提高动力工具100对工件的加工效果，而且还能够使得用户在长期使用动力工具100后也不会感觉到疲劳。
在本实施例中，偏心部131是沿左右方向带动轴承132撞击摆爪133b的，输出轴141也基本是沿左右方向摆动的，因此偏心传动组件13可以被理解为振动源，输出组件14也可以被理解为振动源，或者它们构成的整体被理解为振动源，因此在本实施例中，振动源所产生的振动的激振力方向F与电机轴线103相互垂直。因此，在本实施例中，振动源所产生的振动的激振力方向F也可以被认为是振动主体10所产生的振动的激振力方向F。以下所说的振动主体10所产生的振动的激振力方向F均可以理解为振动源所产生的振动的激振力方向F。
在本实施例中，振动主体10所产生的激振力的激振力方向F与中分面102相互垂直，因此可以设置使得减振***17能够在平行于激振力的激振力方向F且与中分面102垂直的平面内进行隔振，这样能够有效的降低振动主体10沿激振力的激振力方向F传递至非振动主体20的振动。也即是说，减振***17至少部分在沿激振力方向F设置在第一壳体111和第二壳体112之间，或者说，减振***17将第一壳体111和第二壳体112的至少部分在激振力方向F间隔开。
在一些实施例中，振动主体10设有至少两个垂直于电机轴121a的电机轴线103的第一平面和第二平面，减振***17包括：在第一平面上设置的至少一个第一隔振块173以及在第二平面上设置的至少一个第二隔振块174，这里可以将第一平面定义为第一隔振平面171，第二平面定义为第二隔振平面172。在本实施例中，第一隔振块173和第二隔振块174构成的整体中至少具有设置于第一壳体111和第二壳体112之间的间隔部分17a，第二壳体112在间隔部分17a处与第一壳体111间隔开，第一隔振块173和第二隔振块174还相互分离。在一些实施例中，第一隔振块173设置于第一壳体111和第二壳体112之间，第二隔振块174设置于第一壳体111和第二壳体112之间，第二壳体112在第一隔振块173处与第一壳体111间隔开，第二壳体112在第二隔振块174处也与第一壳体111间隔开。第一隔振块173和第二隔振块174相互分离可以理解为第一隔振块173和第二隔振块174非一体成型，它们两者之间间隔开一定的距离。这样，动力工具100中通过设置分隔开的第一隔振块173和第二隔振块174能够提高减振***17的减振效果，从而提高用户的工作效率。在沿垂直于第一隔振 平面171的方向上，第一隔振块173和第二隔振块174相互间隔开。
第一隔振平面171和第二隔振平面172还垂直于振动主体10的中分面102，第一隔振平面171和第二隔振平面172还与振动主体10所产生的激振力的激振力方向F相互平行，第一隔振平面171和第二隔振平面172还与输出轴141的输出轴线105相互平面，输出轴141是在一个垂直于输出轴线105的平面内摆动的，因此第一隔振平面171和第二隔振平面172还与输出轴141摆动的平面相互垂直，第一隔振平面171和第二隔振平面172还与第一直线101相互垂直。这样，第一隔振平面171上的第一隔振块173和第二隔振平面172上的第二隔振块174能够降低振动主体10传递至非振动主体20的振动。在本实施例中，还定义沿第一直线101方向且由第一隔振平面171朝向第二隔振平面172的方向为后，沿第一直线101方向且由第二隔振平面172朝向第一隔振平面171的方向为前。换句话说，我们希望减振***17能够降低振动主体10沿激振力方向F传递至非振动主体20的振动，因此我们还可以这样设置，先定义一个与激振力方向F垂直的隔断平面，而振动主体10设有至少两个均与隔断平面垂直的第一隔振平面172以及第二隔振平面172，第一隔振平面171以及第二隔振平面172上的第一隔振块173以及第二隔振块174能够在沿激振力方向F的方向以及与激振力方向F倾斜相交的方向将振动传递的路径间隔开，从而将振动主体10所产生的振动吸收，进而减小振动主体10沿激振力方向F传递至非振动主体20的振动。
如图4至图6所示，在本实施例中，振动主体10在沿电机轴线103方向上的长度为L，也即是振动主体10沿把手部112a延伸的方向上的长度为L，或者说振动主体10沿垂直于第一隔振平面171的方向上的长度为L。进一步而言，考虑到振动主体10中的电机121、偏心传动组件13、输出组件14以及夹持装置15基本设置在第一壳体111内，因此，在本实施例中，长度L也可以理解为第一壳体111的长度。振动主体10还具有一个重心G，在本实施例，在沿电机轴线103方向上，第一隔振平面171与重心G之间的距离为L1，也即是说，第一隔振平面171与重心G之间的沿电机轴线103方向上的距离为L1，或者说，第一隔振平面171与重心G在沿垂直于第一隔振平面171的方向上的尺寸为L1。在本实施例中，第一隔振平面171与重心G之间的沿电机轴线103方向的距离L1与振动主体10沿电机轴线103方向的长度L的比值大于等于0且小于等于0.3，也即是说，第一隔振平面171与重心G之间沿垂直于第一隔振平面171的 方向上的距离L1与振动主体10沿垂直于第一隔振平面171的方向上的长度L之间的比值大于等于0且小于等于0.3。其中，第一隔振平面171与重心G之间的沿电机轴线103方向的距离L1与振动主体10沿电机轴线103方向的长度L的比值大于等于0且小于等于0.3指的是第一隔振平面171经过重心G或者设置在重心的前侧或者后侧的与重心G间隔0.3L的位置。沿电机轴线103方向上，第一隔振平面171与第二隔振平面172之间的距离为L2，也即是说，第一隔振平面171与第二隔振平面172之间的沿电机轴线103方向的距离为L2，或者说，第一隔振平面171与第二隔振平面172之间的沿垂直于第一隔振平面171的方向的距离为L2。其中，第一隔振平面171与第二隔振平面172之间的沿电机轴线103方向的距离L2与振动主体10沿电机轴线103方向的长度L的比值大于等于0.3且小于等于0.7，也即是说，第一隔振平面171与第二隔振平面172之间的沿垂直于第一隔振平面171的方向上的距离L2与振动主体10沿垂直于第一隔振平面171的方向上的长度L之间的比值大于等于0.3且小于等于0.7。这样能够使得第二隔振平面172的位置设置的更为合理，从而能够更好的提高减振***17的减振效果。第二隔振平面172的位置设置合理，一方面能够提高减振***17的减振效果，另一方面还能够更稳定的对第一壳体111和第二壳体112构成支撑。
在一些实施例中，第一隔振平面171位于重心G的前侧，且第一隔振平面171与重心G之间的沿电机轴线103方向的距离L1与振动主体10沿电机轴线103方向的长度L的比值大于等于0.2且小于等于0.3，其中，本实施例中的“之间”包含端点位置；或者，第一隔振平面171位于重心G的前侧，且第一隔振平面171与重心G之间的沿电机轴线103方向的距离L1与振动主体10沿电机轴线103方向的长度L的比值大于等于0.1且小于等于0.2，从而提高减振***17的减振效果；或者，第一隔振平面171位于重心G的前侧，且第一隔振平面171与重心G之间的沿电机轴线103方向的距离L1与振动主体10沿电机轴线103方向的长度L的比值大于等于0.05且小于等于0.1，从而提高减振***17的减振效果；或者，第一隔振平面171位于重心G的前侧，且第一隔振平面171与重心G之间的沿电机轴线103方向的距离L1与振动主体10沿电机轴线103方向的长度L的比值大于等于0且小于等于0.05，从而提高减振***17的减振效果；或者，第一隔振平面171与重心G之间的沿电机轴线103方向的距离L1与振动主体10沿电机轴线103方向的长度L的比值大于等于0且小于等于0.1， 也即是说，第一隔振平面171位于重心G的前侧的0.1L到后侧的0.1L之间；或者，第一隔振平面171与重心G之间的沿电机轴线103方向的距离L1与振动主体10沿电机轴线103方向的长度L的比值大于等于0且小于等于0.05，也即是说，第一隔振平面171位于重心G的前侧的0.05L到后侧的0.05L之间，从而使得第一隔振平面171更靠近重心G，从而提高减振***17的减振效果；或者，第一隔振平面171位于重心G的后侧，第一隔振平面171与重心G之间的沿电机轴线103方向的距离L1与振动主体10沿电机轴线103方向的长度L的比值大于等于0且小于等于0.1，从而提高减振***17的减振效果；或者，第一隔振平面171位于重心G的后侧，且第一隔振平面171与重心G之间的沿电机轴线103方向的距离L1与振动主体10沿电机轴线103方向的长度L的比值大于等于0.1且小于等于0.3，从而提高减振***17的减振效果。而第一隔振平面171和第二隔振平面172之间的在沿电机轴线103方向上的距离L2与振动主体10沿电机轴线103方向的长度L的比值大于等于0.3且小于等于0.4；或者，第一隔振平面171和第二隔振平面172之间的在沿电机轴线103方向上的距离L2与振动主体10沿电机轴线103方向的长度L的比值大于等于0.4且小于等于0.5；或者，第一隔振平面171和第二隔振平面172之间的在沿电机轴线103方向上的距离L2与振动主体10沿电机轴线103方向的长度L的比值大于等于0.5且小于等于0.7。其中，需要说的是，上述第一隔振平面171与重心G之间的沿电机轴线103方向的距离L1与振动主体10沿电机轴线103方向的长度L的比值的任意一个取值范围可以和第一隔振平面171和第二隔振平面172之间的在沿电机轴线103方向上的距离L2与振动主体10沿电机轴线103方向的长度L的比值的任意一个取值范围进行组合，这样的任意种组合均能使得减振***17达到不错的减振效果。需要说明的是，将第一隔振平面171设置在重心G的前侧，第二隔振平面172设置在重心G的后侧，也即是说将重心G设置在第一隔振平面171和第二隔振平面172之间，能够进一步的提高减振效果；而且第一隔振平面171与第二隔振平面172之间的距离的不同也会影响减振效果，而在本实施例中，将第一隔振平面171和第二隔振平面172之间的距离设置在一个合理的范围内，从而使得动力工具100的减振效果达到最佳。
在本实施例中，在沿电机轴线103方向上，重心G与振动源134之间的距离大于等于0且小于等于0.2L，也即是说，在沿电机轴线103上重心G尽可能的靠近振动源134,从而当第一隔振平面171靠近重心G设置时，能够隔振振动 主体10产生的主要的振动量，而通过设置第二隔振平面172能够进一步的隔振振动主体10的其它振动量，进而能够更好提高减振***17的减振效果。
在一些实施例中，第一隔振平面171上设置有两个第一隔振块173，第一隔振块173设置在头壳111b上，也即是说，头壳111b上设置有两个第一隔振块173，这两个第一隔振块173还分别设置在中分面102的两侧。第一隔振块173具有一个大小为K的正向刚度，第一隔振块173的正向刚度的方向为D。其中，第一隔振块173的正向刚度的方向D与激振力的激振力方向F之间的夹角大于等于0度且小于等于60度，在一些实施例中，第一隔振块173的正向刚度的方向D与激振力的激振力方向F之间的夹角大于等于0度且小于等于45度，在一些实施例中，第一隔振块173的正向刚度的方向D与激振力的激振力方向F之间的夹角大于等于0度且小于等于30度，在一些实施例中，第一隔振块173的正向刚度的方向D与激振力的激振力方向F之间的夹角大于等于0度且小于等于10度，在一些实施例中，还可以使得至少一个第一隔振块173的正向刚度的方向D与激振力的激振力方向F平行。在一些实施例中，可以使得至少一个第一隔振块173设置在激振力方向F在第一隔振平面171的正投影上。这样，能够使得第一隔振块173的正向刚度的方向D尽可能的靠近激振力的激振力方向F，从而能够更好的提高减振***17的减振效果。
第一隔振块173的正向刚度的方向D与激振力的激振力方向F之间的夹角大于等于0度且小于等于15度；或者，第一隔振块173的正向刚度的方向D与激振力的激振力方向F之间的夹角大于等于15度且小于等于30度；或者，第一隔振块173的正向刚度的方向D与激振力的激振力方向F之间的夹角大于等于30度且小于等于45度；或者，第一隔振块173的正向刚度的方向D与激振力的激振力方向F之间的夹角大于等于45度且小于等于60度。
在一些实施例中，对于本实施例的摆动类工具而言，第一隔振块173设置在一个垂直于中分面102且经过电机轴线103的平面内，也即是说，第一隔振块173的正向刚度的方向D与偏心部131运动的左右方向相互平行。这样，能够更优的提高减振***17的减振效果。
在本实施例中，第二隔振平面172上第二隔振块174的数目至少为两个以上。第一隔振平面171上的多个第一隔振块173在垂直于电机轴线103的平面内的正投影与第二隔振平面172上的多个第二隔振块174在垂直于电机轴线103的平面内的正投影至少部分是交错设置的，第一隔振平面171上的多个第一隔 振块173在垂直于电机轴线103的平面内的正投影与第二隔振平面172上的多个第二隔振块174在垂直于电机轴线103的平面内的正投影也可以完全交错，该平面也与第一隔振平面171平行。在一些实施例中，第一隔振平面171上的多个第一隔振块173在垂直于电机轴线103的平面内的正投影与第二隔振平面172上的多个第二隔振块174在垂直于电机轴线103的平面内的正投影在沿围绕电机轴线103的圆周方向上至少部分是交错设置的。或者说，第一隔振平面171上的多个第一隔振块173在垂直于电机轴线103的平面内的正投影为多个第一投影，第二隔振平面172上的多个第二隔振块174在垂直于电机轴线103的平面内的正投影为多个第二投影，其中，多个第一投影中的至少部分与多个第二投影中的至少部分在围绕电机轴线103的圆周方向上是依次交错设置的。在一些实施例中，第一隔振平面171上的多个第一隔振块173在垂直于电机轴线103的平面内的正投影与第二隔振平面172上的多个第二隔振块174在垂直于电机轴线103的平面内的正投影在沿围绕电机轴线103的圆周方向上是依次交错设置的。这样，当第一隔振平面171上的第一隔振块173尽可能的吸收振动主体10沿激振力的激振力方向F上的振动，第二隔振平面172上的第二隔振块174能够尽可能的吸收振动主体10沿除了激振力的激振力方向F之外的其它方向的振动，从而能够更好的提高减振***17的减振效果。在一些实施例中，第二隔振块174安装至电机121壳体上。对于本实施例的摆动类工具而言，无论是偏心部131对摆杆133的撞击方向还是输出轴141摆动的方向均是基本与激振力方向F平行，且偏心部131对摆杆133的撞击方向以及输出轴141摆动的方向均是基本与电机轴线103相互垂直，因此将第一隔振块173以及第二隔振块174设置在垂直于电机轴线103的平面内，能够有效的降低偏心部131对摆杆133的撞击而产生的主要振动，也能够降低输出轴141摆动所产生的次要振动。
在本实施例中，第一隔振块173的数目为两个或者两个以上，第一隔振块173在围绕电机轴线103的圆周方向上依次排列，且在圆周方向上，相邻的两个第一隔振块173之间还具有间隙，也即是说，任意两个第一隔振块173之间是间隔开的；第二隔振块174的数目为两个或者两个以上，第二隔振块174在围绕电机轴线103的圆周方向上依次排列，且在圆周方向上，相邻的两个第二隔振块174之间还具有间隙，也即是说，任意两个第二隔振块174之间是间隔开的。这样，能够从多个方向对振动主体10所产生的振动进行隔振，提高减振效果。
需要说明的是，在本实施例中，第一隔振平面171上通过多个间隔设置的第一隔振块173来实现减振效果，可以理解的，在其它实施例中，第一隔振平面171上也可也通过设置沿围绕电机轴线103的圆周方向延伸的环形的隔振块来实现隔振。同样的，第二隔振平面172上通过多个间隔设置的第二隔振块174来实现减振效果，可以理解的，在其它实施例中，第二隔振平面172上也可也通过设置沿围绕电机轴线103的圆周方向延伸的环形的隔振块来实现隔振。而且，在本实施例中，将第一隔振平面171以及第二隔振平面172间隔开，也即是第一隔振块173和第二隔振块174在沿垂直于第一隔振平面171的方向间隔开，这样一方面能够在使用尽可能少的隔振块的前提下提高隔振效果，另一方面还使得第一壳体111的位于第一隔振平面171以及第二隔振平面172之间的部分与第二壳体112的位于第一隔振平面171以及第二隔振平面172之间的部分之间设置间隙，从而能够进一步地阻碍第一壳体111传递至第二壳体112的振动。在一些实施例中，第一壳体111的位于第一隔振平面171以及第二隔振平面172之间的部分与第二壳体112的位于第一隔振平面171以及第二隔振平面172之间的部分之间设置的间隙为围绕电机轴线103的环形间隙。
在一些实施例中，第二隔振平面172上的第二隔振块174设置在电机壳体部111d上，也即是说，第二隔振平面172经过电机壳体部111d。
可以理解的，在本文中，振动主体10还包括垂直于电机轴121a的电机轴线103的第三隔振平面175，第三隔振平面175上设有第三隔振块，第三隔振平面175还设置于第一隔振平面171和第二隔振平面172之间。
在本实施例中，第一隔振块173、第二隔振块174以及第三隔振块均采用聚氨酯发泡材料制成，其弹性好，恢复性能好。第一隔振块173或者第二隔振块174还设置在把手部112a内，从而能够进一步的减少传递至用户的手的振动。电机壳体部111d与第二壳体112之间具有间隙，第二隔振块174设置在间隙中。
在本实施例中，动力工具100在启动后且空载时经过测量能够得到一个振动加速度，该振动加速度的值为a米/秒^2，这样在动力工具100的减振效果被提高的前提下，我们可以使得动力工具100的切割能力能够得到大幅度的提高。具体而言，对于摆动类工具而言，电机121的最大的转速为R转/分，输出轴141的摆动角度为A度，其中，电机121的转速R与动力工具100的振动加速度a的比值大于等于5000且小于等于20000。输出轴141的摆动角度A与动力工具100的振动加速度a的比值大于等于1且小于等于3。在一些实施例中，电机121 的转速R与动力工具100的振动加速度a的比值大于等于5000且小于等于6000，或者，电机121的转速R与动力工具100的振动加速度a的比值大于等于6000且小于等于10000，或者，电机121的转速R与动力工具100的振动加速度a的比值大于等于10000且小于等于20000。输出轴141的摆动角度A与动力工具100的振动加速度a的比值大于等于1且小于等于1.7；或者，输出轴141的摆动角度A与动力工具100的振动加速度a的比值大于等于1.7且小于等于3。这样，对于振动幅度比较大的动力工具100而言，当该动力工具100的振动问题被解决时，则可以进一步的使得动力工具100的输出效率得到提高，从而满足人们日益增长的对低振动的动力工具100的需求，也大大地促进了动力工具100的发展。更具体而言，根据我们适当的调整减振***17的结构、性能以及位置等，从而可以使得电机121的转速R可以大于等于20000且小于等于22000，或者还可以使得电机121的转速R大于等于22000，输出轴141的摆动角度A可以大于等于3.6且小于等于5，或者，输出轴141的摆动角度A还可以大于等于5。
本文中，该动力工具的振动被较好的控制，从而能够提高用户的工作效率。

Claims (20)

  1. 一种动力工具，包括：
    动力组件，包括电机，所述电机包括能绕电机轴线转动的电机轴；
    输出组件，包括设置为输出动力的输出轴；
    传动组件，设置为在所述动力组件和输出组件之间实现动力的传递；
    第一壳体，至少能支撑所述动力组件、传动组件和输出组件；
    第二壳体，对所述第一壳体至少部分进行包围，所述第二壳体还形成有设置为供用户握持的把手部；
    其中，所述动力工具设置有第一隔振平面和第二隔振平面，所述第一隔振平面上设置有第一隔振块，所述第二隔振平面设置有第二隔振块；所述第一隔振块和所述第二隔振块构成的整体中至少具有设置于所述第一壳体和所述第二壳体之间的间隔部分，所述第二壳体在所述间隔部分处与所述第一壳体间隔开；所述第一隔振块和所述第二隔振块相互分离。
  2. 根据权利要求1所述的动力工具，其中，定义所述动力工具中产生振动的结构为振动主体，所述振动主体至少包括所述动力组件、输出组件、传动组件以及第一壳体，所述振动主体具有一个重心，所述振动主体在沿所述电机轴线方向上的长度为L；
    所述第一隔振平面与所述电机轴线相互垂直，所述第一隔振平面与所述振动主体的重心之间的沿所述电机轴线方向上的距离为L1；其中，所述第一隔振平面与所述振动主体的重心之间的沿所述电机轴线方向上的距离L1与所述振动主体在沿所述电机轴线方向上的长度L的比值大于等于0且小于等于0.3。
  3. 根据权利要求2所述的动力工具，其中，所述第二隔振平面与所述电机轴线相互垂直，所述第一隔振平面与所述第二隔振平面之间的距离为L2；所述第一隔振平面与所述第二隔振平面之间的距离L2与所述振动主体在沿所述电机轴线方向上的长度L的比值大于等于0.3且小于等于0.7。
  4. 根据权利要求2所述的动力工具，其中，所述振动主体的重心位于所述第一隔振平面和所述第二隔振平面之间。
  5. 根据权利要求2所述的动力工具，其中，所述振动主体还定义有垂直于所述电机轴线的第三隔振平面，所述第三隔振平面上设置有第三隔振块，所述第三隔振平面设置在所述第一隔振平面和所述第二隔振平面之间。
  6. 根据权利要求1所述的动力工具，其中，所述第一壳体和所述第二壳体相互间隔开，所述第一隔振块设置于所述第一壳体和所述第二壳体之间，所述 第二隔振块设置于所述第一壳体和所述第二壳体之间。
  7. 根据权利要求1所述的动力工具，其中，所述第一隔振平面和所述第二隔振平面相互平行，所述第一隔振块和所述第二隔振块在沿垂直于第一隔振平面的方向上相互间隔开。
  8. 根据权利要求1所述的动力工具，其中，所述第一壳体关于一个中分面对称，所述第一隔振块的数目至少为两个，所述第一隔振块对称的分布在所述中分面的两侧。
  9. 根据权利要求1所述的动力工具，其中，至少部分所述第一隔振块或者至少部分所述第二隔振块设置在所述把手部内。
  10. 根据权利要求1所述的动力工具，其中，所述第一隔振平面和所述第二隔振平面相互平行，所述第二隔振平面上的第二隔振块在一个与所述第一隔振平面平行的平面内的正投影与所述第一隔振平面上的第一隔振块在该平面上的正投影是至少部分交错的。
  11. 根据权利要求1所述的动力工具，其中，
    所述第一壳体包括：
    电机壳体部，设置为支撑所述电机；
    头壳，设置为支撑所述输出轴；
    所述头壳设置在所述电机壳体部的前侧并与所述电机壳体部构成固定连接；
    所述第一隔振块安装至所述头壳。
  12. 根据权利要求11所述的动力工具，其中，所述第二隔振块安装至所述电机壳体部。
  13. 根据权利要求12所述的动力工具，其中，所述电机壳体部和所述第二壳体之间具有间隙，所述第二隔振块设置在所述间隙中。
  14. 根据权利要求1所述的动力工具，其中，所述输出轴能以所述输出轴线为中心在摆动角度A度内摆动；所述输出轴的摆动角度A大于等于3.6且小于等于5。
  15. 根据权利要求1所述的动力工具，其中，所述电机具有最大的转速R转/分，所述电机的最大的转速R大于等于20000且小于等于22000。
  16. 根据权利要求1所述的动力工具，其中，所述第一隔振块的数目为两个以上，这些第一隔振块在围绕所述电机轴线的圆周方向上依次排列；且在该 圆周方向上，相邻的两个第一隔振块之间具有间隙。
  17. 根据权利要求1所述的动力工具，其中，所述输出轴能以所述输出轴线为中心在摆动角度A度内摆动；所述传动组件包括：撞击部和能被所述撞击部沿激振力方向F撞击的摆杆；至少一个所述第一隔振块的正向刚度方向D与所述激振力方向F之间形成角度大于等于0度且小于等于60度的夹角。
  18. 根据权利要求17所述的动力工具，其中，至少一个所述第一隔振块的正向刚度方向D与所述激振力方向F平行。
  19. 根据权利要求1所述的动力工具，其中，所述第一隔振块采用聚氨酯发泡材料制成。
  20. 根据权利要求1所述的动力工具，其中，所述动力工具包括至少两个所述第一隔振块；所述动力工具包括至少两个所述第二隔振块。
PCT/CN2019/089844 2018-06-05 2019-06-03 动力工具 WO2019233380A1 (zh)

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