CN108488285B - Electric tool and spring thereof - Google Patents
Electric tool and spring thereof Download PDFInfo
- Publication number
- CN108488285B CN108488285B CN201810559123.7A CN201810559123A CN108488285B CN 108488285 B CN108488285 B CN 108488285B CN 201810559123 A CN201810559123 A CN 201810559123A CN 108488285 B CN108488285 B CN 108488285B
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- China
- Prior art keywords
- spring
- power tool
- thickness
- gap
- hook
- Prior art date
- Legal status (The legal status 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 status listed.)
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Links
- 238000005452 bending Methods 0.000 claims description 17
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 claims description 9
- 229910052799 carbon Inorganic materials 0.000 claims description 9
- 238000000034 method Methods 0.000 claims description 8
- 238000002788 crimping Methods 0.000 claims description 2
- WYTGDNHDOZPMIW-RCBQFDQVSA-N alstonine Natural products C1=CC2=C3C=CC=CC3=NC2=C2N1C[C@H]1[C@H](C)OC=C(C(=O)OC)[C@H]1C2 WYTGDNHDOZPMIW-RCBQFDQVSA-N 0.000 description 4
- 230000007812 deficiency Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F1/00—Springs
- F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
- F16F1/04—Wound springs
- F16F1/10—Spiral springs with turns lying substantially in plane surfaces
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F1/00—Springs
- F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
- F16F1/04—Wound springs
- F16F1/12—Attachments or mountings
- F16F1/123—Attachments or mountings characterised by the ends of the spring being specially adapted, e.g. to form an eye for engagement with a radial insert
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Springs (AREA)
Abstract
The application provides an electric tool and a spring thereof. A spring (100) for a power tool includes: a body (110) comprising a multi-turn convolution, an inner hook (130) connected to an innermost turn (112) of the convolution for securing the spring (100) to the power tool; and an outer hook (120) connected to the outermost ring (111) of the spiral structure for providing a pressing force to the power tool. A gap greater than the thickness of the material of the spring (100) is provided between adjacent ring opposing portions of the body (110), and the body (110) has a gap narrowing portion (113) smaller than the thickness of the material of the spring (100) at least between one adjacent ring opposing portion.
Description
Technical Field
The present invention relates to a spring for a power tool and a power tool with such a spring.
Background
Various electric tools, particularly portable electric tools, are widely used. In the use of power tools, the pressing of components in the power tool is typically accomplished with springs.
A spring is a mechanical part that works with elasticity. The kinds of springs are complex and diverse, in which the coil springs can continuously provide a large restoring force in a small space and have a characteristic of being not easily fatigued, and thus the coil springs are widely used in electric tools. The coil spring structurally comprises a serpentine multi-turn serpentine structure, with the spring material forming the serpentine structure being elastically deformed by bending during operation. However, when a relatively large number of such springs are mixed together and packed in a single package, the springs will be stuck to each other due to the gaps between the convolutions of the springs. Before using such springs on a power tool, the springs must be separated from each other, which is time consuming and labor intensive.
Accordingly, there is a need for an improved spring for a power tool that overcomes the deficiencies of the prior art.
Disclosure of Invention
In view of the above technical problems, the present application provides an improved spring for a power tool and a power tool with the spring, which has simple structure, low cost and easy operation.
To this end, according to one aspect of the present application, there is provided a spring for a power tool. The spring includes: a body including a multi-turn convolution, an inner hook connected to an innermost turn of the convolution for securing the spring to the power tool; and the outer hook part is connected with the outermost ring of the spiral structure and is used for providing a pressing force for the electric tool. The body has a gap between adjacent coil opposing portions that is greater than a thickness of material of the spring, and the body has a gap narrowing between at least one adjacent coil opposing portion that is less than the thickness of material of the spring.
According to one possible embodiment, the gap constriction is configured to: the gap between two adjacent turns of the multi-turn spiral structure has a gap portion smaller than the thickness of the material of the spring, and the gap narrowing portion is formed by a separate process other than the crimping process of the body.
According to one possible embodiment, the gap narrowing portion is formed by a punch-rivet process or a large-angle bending process.
According to one possible embodiment, the inner hook portion includes a bent portion formed by bending at one end of the innermost ring, and the gap narrowing portion is configured to: the radial distance between the bending point of the bending part and the facing part of the innermost ring is smaller than the thickness of the material of the spring.
According to one possible embodiment, the gap constriction is configured to: the radial distance between the end of the bent portion and the facing portion of the innermost ring is smaller than the thickness of the material of the spring.
According to a possible embodiment, the innermost ring portion of the inner hook has a protrusion, the radial distance between the protrusion and the facing location of its adjacent turn being less than the thickness of the material of the spring.
According to one possible embodiment, the outer hook is a V-shaped outer hook having a reverse bend at the end of the outer hook, the multi-turn spiral, the inner hook, the outer hook and the reverse bend being formed as a unitary structure.
According to one possible embodiment, the spring is a flat spiral spring.
According to one possible embodiment, the spring (100) provides a pressing force for a carbon brush in the electric tool.
According to one possible embodiment, the power tool is an angle grinder.
According to the application, one end of the spring is fixedly attached to the electric tool, the other end is in contact connection with the electric tool, and the torque force is utilized to provide the pressing force for the electric tool.
Drawings
The foregoing and other aspects of the application will be more fully understood and appreciated from the following detailed description, taken in conjunction with the accompanying drawings, in which:
fig. 1 shows a schematic view of a state in which a spring according to one possible embodiment of the present application is provided in a power tool.
Fig. 2 shows a schematic structural view of a spring according to one possible embodiment of the application.
Fig. 3 shows a schematic structural view of a spring according to another possible embodiment of the application.
Fig. 4 shows a schematic structural view of a spring according to yet another possible embodiment of the application.
Detailed Description
Some embodiments of the present application will now be described with reference to the accompanying drawings.
The present application relates generally to power tools having springs disposed therein. The power tool is in particular a portable power tool, such as a circular saw, angle grinder, grinder or the like. The spring is provided in the power tool, and the spring force thereof is utilized to provide a pressing force to the components in the power tool. For example, a spring is disposed in a motor of the electric tool, and one end of the spring is in contact connection with a carbon brush of the motor to provide a pressing force to the carbon brush.
Fig. 1 shows a schematic state of a spring for a power tool according to one possible embodiment of the present application. As shown in fig. 1, the spring 100 is coiled by a flat wire and is mounted in a power tool. One end 130 of the spring 100 is used to secure the spring 100 to the stationary shaft 1 of the power tool. The other end 120 of the spring 100 is connected in contact with the carbon brush 2 of the motor of the electric tool. Here, the carbon brush 2 is located below the end 120 of the spring and is connected to the wire L of the power tool. The end 120 is applied with torque, and the material of the spring 100 is elastically deformed by bending under the action of the torque, so that the spring 100 is twisted in a plane, and the deformation angle is proportional to the torque, so that the spring 100 can provide the pressing force F to the carbon brush 2 in contact with the end 120. The direction of the pressing force F is shown by the arrow in fig. 1. Although spring 100 is illustrated in fig. 1 as being coiled from a flat wire, it should be appreciated that spring 100 may be coiled from other forms of wire, and is not so limited.
Next, a specific structure of the spring will be described with reference to fig. 1 and 2.
Fig. 2 shows a schematic structural view of a spring according to one possible embodiment of the application. As shown in fig. 2, the spring 100 has a substantially flat shape, and includes: a body 110 and an outer hook 120. The body (110) includes a multi-turn convolution and an inner hook (130) connected to an innermost turn (112) of the convolution for securing the spring (100) to the power tool.
The body 110 includes a multi-turn serpentine structure. Here, the number of turns of the spiral structure may be set according to a specific application. The convolutions may be multi-turn convolutions of the material of the spring 100 about the same center of a circle in a plane. In some embodiments, the turns of the convolutions are equally spaced. It should be understood that when the material used to coil spring 100 is a flat wire, the thickness of the material of spring 100 refers to the thickness of the flat wire. When the material used to coil the spring 100 is a round wire, the thickness of the material of the spring 100 refers to the diameter of the round wire. Of course, the material of the spring 100 is not limited thereto, and may be any suitable type.
In some embodiments, adjacent turns of the body (110) have a gap between them that is greater than the thickness of the material of the spring (100), and the multi-turn convolutions have a gap constriction 113 between at least one adjacent turn of the opposite, location that is less than the thickness of the material of the spring 100. For example, in the annular gap between adjacent turns of the convolutions, there is a gap constriction 113 that is less than the thickness of the material of the spring 100. In the spiral structure, the gap narrowing portion 113 smaller than the thickness of the material of the spring 100 has at least one place, and may have two or more places. That is, in the annular gap of the spiral structure, there is a gap narrowing portion (at least smaller than the thickness of the material of the spring) small enough that this gap (pitch) cannot be caught in another spring, and thus, when a plurality of such springs are put together, they do not have a problem of being caught in each other.
With continued reference to fig. 2, the body 100 includes an inner hook 130. The inner hook 130 includes a portion of the innermost ring 112 of the spiral structure and a bent portion 131 formed by bending at one end of the innermost ring 112. In some embodiments, the portion of the inner most loop 112 of the inner hook 130 forms a generally semi-circular structure with the bend 131. In some embodiments, the bend 131 is a hook bent at one end of the innermost ring 112 of the convolution. The bending angle α of the bending portion 131 is preferably 90 ° so as to be stably fixed to the fixed shaft 1 of the power tool, and is not liable to shake. Of course, the bending angle α of the bending portion may be other suitable angles. The inner hook 130 secures the spring 100 to the power tool with its hooked bent structure. For example, as shown in fig. 1, the bending portion 131 is engaged with the fixed shaft 1 of the power tool.
The outer hook 120 may be a V-shaped hook connected to one end of the outermost ring 111 of the spiral structure. For example, the outer hook 120 is tangentially connected to the outermost ring 111. The outer hook 120 is in contact with a component of the power tool, for example, the outer hook 120 is pressed over the carbon brush 2 of the motor of the power tool, while the inner hook 130 is engaged on the fixed shaft 1 of the power tool, so that the outer hook 120 generates a torque force, thereby realizing that the spring 100 provides a pressing force (e.g., a pressure F in fig. 1) to the carbon brush 2 in contact therewith.
In some embodiments, the outer hook 120 has a reverse bend 121 at its end to prevent its end from damaging components in the power tool by being too sharp. Of course, other structures may be employed at the distal end of the outer hook 120 to prevent the distal end from being too sharp to damage components in the power tool.
With continued reference to fig. 2, the radial distance between the inflection point P1 of the inflection 131 of the inner hook 130 and the facing location of the innermost ring 112 of the convolution is less than the thickness of the material of the spring 100, even zero. In some embodiments, the material used for the coil spring 100 is a material of approximately equal thickness. Of course, in the case where the thicknesses of the materials used to coil the spring 100 are not equal, the distance should be less than the minimum thickness of the material of the spring 100. That is, the inner hook portion of such a spring is structured such that the radial distance between it and the facing portion of the innermost ring of the spring is sufficiently small (at least smaller than the thickness of the material of the spring) that this distance (gap) cannot be caught in another spring, whereby when a plurality of such springs are put together, they do not have a problem of being caught in each other.
As can be seen from the above description, in the case where a large number of springs 100 according to the present application are stacked together, any two springs do not overlap each other due to the structure of the bent portion 131 of the inner hook 130. Thus, when the spring is used for working on the electric tool, the work of separating the spring from the electric tool is omitted, and the working efficiency is improved. Also, the structure of the inner hook 130 does not change the torque generated when the spring 100 is twisted. That is, the spring force of the spring 100 is unchanged, so that the pressing force provided by the spring 100 to the power tool is also unchanged.
Fig. 3 shows a schematic structural view of a spring according to another possible embodiment of the invention. The spring 100' shown in fig. 3 differs from the spring 100 shown in fig. 2 only in the structure of the inner hook 130' of the spring 100', and the other parts are the same as the spring 100 shown in fig. 1. For clarity, no further description is provided herein. In this implementation, the radial distance between the end P2 of the bent portion 131' of the inner hook 130' and the facing portion of the innermost ring 112 of the spiral is less than the thickness of the material of the spring 100', even zero. That is, the inner hook 130' is structured such that the radial distance from the facing portion of the innermost ring of the springs is sufficiently small (at least less than the thickness of the material of the springs) that this distance (gap) cannot be snapped into another spring, whereby when a plurality of such springs are placed together, they do not present a problem of snapping one another.
As can be seen from the above description, in the case where a large number of springs 100 according to the present application are stacked together, any two springs do not overlap each other due to the structure of the bent portion 131 'of the inner hook 130'. Thus, when the spring is used for working on the electric tool, the work of separating the spring from the electric tool is omitted, and the working efficiency is improved. Also, the structure of the inner hook 130' does not change the torque generated by the spring 100 when it is twisted. That is, the spring force of the spring 100 is unchanged, so that the pressing force provided by the spring 100 to the power tool is also unchanged.
Of course, in some implementations, the inner hook of the spring may also be configured to: the radial distance between the bending point of the bending part and the facing part of the innermost ring of the spiral structure is smaller than the thickness of the material of the spring, and the radial distance between the tail end of the bending part and the facing part of the innermost ring of the spiral structure is smaller than the thickness of the material of the spring. That is, in some implementations, the structure of the inner hook of the spring 100 may be configured such that the spring 100 has two or more gap constrictions 113 that are less than the thickness of the material of the spring 100.
Fig. 4 shows a schematic structural view of a spring according to yet another possible embodiment of the invention. The spring 100 "shown in fig. 4 differs from the spring 100 shown in fig. 2 only in the structure of the inner hook 130" of the spring 100", and the other parts are the same as the spring 100 shown in fig. 1. For clarity, no further description is provided herein. In this implementation, the innermost portion of the inner hook 130 "has a protrusion 132. The protrusion 132 protrudes outward (away from the center) from somewhere in the innermost ring 112 such that the radial distance between the protrusion 132 and the facing location of its adjacent ring is less than the thickness of the material of the spring. That is, the protrusion 132 allows the spring 100 to have a gap (at least less than the thickness of the material of the spring) that is small enough that it cannot be snapped into another spring, and thus, when a plurality of such springs are placed together, they do not present a problem of snapping one another. Also, the structure of the inner hook 130″ does not change the torque generated when the spring 100 is twisted. That is, the spring force of the spring 100 is unchanged, so that the pressing force provided by the spring 100 to the power tool is also unchanged.
It should be understood that the inner hook of the spring according to the application may also be configured in other ways. The various arrangements of the inner hooks do not change the torque generated by the spring 100 when it is twisted or do not change the torque generated by the spring 100 when it is twisted as much as possible. That is, various arrangements of the inner hook portion may not change the spring force of the spring, so that the pressing force provided by the spring to the power tool may not change.
In some embodiments, the spring according to the present application is a coil spring, such as a flat spiral spring.
It will be appreciated that the various parts of the spring according to the application can be adapted according to the application.
It will be apparent to those skilled in the art that the spring of the present application may be applied to power tools requiring such springs, for example, angle grinders and the like.
Although the application is described herein with reference to specific embodiments, the scope of the application is not intended to be limited to the details shown. Various modifications may be made to these details without departing from the underlying principles of the application.
Claims (8)
1. A spring (100) for a power tool, the spring (100) comprising:
A body (110) including a multi-turn spiral structure and an inner hook (130) connected to an innermost ring (112) of the spiral structure for fixing the spring (100) to the power tool, the inner hook (130) including a bent portion (131) formed by bending at one end of the innermost ring (112);
An outer hook (120) connected to an outermost ring (111) of the spiral structure for providing a pressing force to the power tool;
Wherein adjacent turns of the body (110) have a gap between them that is greater than the thickness of the material of the spring (100), the body (110) has a gap constriction (113) between at least one adjacent turn of the opposite ends that is less than the thickness of the material of the spring (100), and
Wherein the gap constriction (113) has at least one of the following features:
-the gap between two adjacent turns of the multi-turn convolutions has a gap portion smaller than the thickness of the material of the spring (100);
-the radial distance between the inflection point (P1) of the inflection (131) and the facing location of the innermost ring (112) is smaller than the thickness of the material of the spring (100); and
-The radial distance between the end of the bend (131) and the facing portion of the innermost ring (112) is smaller than the thickness of the material of the spring (100).
2. The spring (100) according to claim 1, wherein the gap narrowing portion (113) is formed by a separate process other than the crimping process of the body (110).
3. The spring (100) according to claim 2, wherein the gap narrowing portion (113) is formed by a caulking process or a large angle bending process.
4. A spring (100) according to any one of claims 1 to 3, wherein the innermost portion of the inner hook (130) has a protrusion (132), the radial distance between the protrusion (132) and the facing location of its adjacent turn being less than the thickness of the material of the spring (100).
5. A spring (100) according to any one of claims 1 to 3, wherein the outer hook (120) is a V-shaped outer hook, having a reverse bend (121) at the end of the outer hook (120), the multi-turn spiral, the inner hook (130), the outer hook (120) and the reverse bend (121) being formed as a unitary structure.
6. A spring (100) according to any one of claims 1-3, wherein the spring (100) is a flat spiral spring.
7. A power tool, characterized in that the power tool comprises a spring (100) according to any one of claims 1-6, the spring (100) providing a pressing force for carbon brushes in the power tool.
8. The power tool of claim 7, wherein the power tool is an angle grinder.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810559123.7A CN108488285B (en) | 2018-06-01 | 2018-06-01 | Electric tool and spring thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810559123.7A CN108488285B (en) | 2018-06-01 | 2018-06-01 | Electric tool and spring thereof |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108488285A CN108488285A (en) | 2018-09-04 |
| CN108488285B true CN108488285B (en) | 2024-05-14 |
Family
ID=63341821
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810559123.7A Active CN108488285B (en) | 2018-06-01 | 2018-06-01 | Electric tool and spring thereof |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN108488285B (en) |
Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH09257070A (en) * | 1996-03-21 | 1997-09-30 | Hayashi Spring Seisakusho:Kk | Spiral spring |
| CN102203453A (en) * | 2008-09-22 | 2011-09-28 | 日本泰克尼卡株式会社 | Spiral spring |
| CN203756826U (en) * | 2014-01-20 | 2014-08-06 | 浙江汇泽机械科技有限公司 | Easily assembled volute spiral spring |
| CN104067019A (en) * | 2012-01-25 | 2014-09-24 | 中央发条株式会社 | Spiral spring |
| DE102013226137A1 (en) * | 2013-12-17 | 2015-06-18 | Schaeffler Technologies AG & Co. KG | Spiral spring winding with partially different winding spacings for local elimination of the winding contact of the individual windings |
| CN104879408A (en) * | 2015-06-18 | 2015-09-02 | 上海协力卷簧制造有限公司 | Contact flat spiral spring device |
| CN205956275U (en) * | 2016-08-17 | 2017-02-15 | 诸暨市康宇弹簧有限公司 | Spiral spring |
| CN205978213U (en) * | 2016-07-25 | 2017-02-22 | 重庆长安汽车股份有限公司 | Coil spring underlay structure |
| CN206889543U (en) * | 2017-07-07 | 2018-01-16 | 泰州市创新电子有限公司 | A kind of multilaminate coiled spring and its lifting support |
| CN208331072U (en) * | 2018-06-01 | 2019-01-04 | 博世电动工具（中国）有限公司 | Electric tool and its spring |
-
2018
- 2018-06-01 CN CN201810559123.7A patent/CN108488285B/en active Active
Patent Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH09257070A (en) * | 1996-03-21 | 1997-09-30 | Hayashi Spring Seisakusho:Kk | Spiral spring |
| CN102203453A (en) * | 2008-09-22 | 2011-09-28 | 日本泰克尼卡株式会社 | Spiral spring |
| CN104067019A (en) * | 2012-01-25 | 2014-09-24 | 中央发条株式会社 | Spiral spring |
| DE102013226137A1 (en) * | 2013-12-17 | 2015-06-18 | Schaeffler Technologies AG & Co. KG | Spiral spring winding with partially different winding spacings for local elimination of the winding contact of the individual windings |
| CN203756826U (en) * | 2014-01-20 | 2014-08-06 | 浙江汇泽机械科技有限公司 | Easily assembled volute spiral spring |
| CN104879408A (en) * | 2015-06-18 | 2015-09-02 | 上海协力卷簧制造有限公司 | Contact flat spiral spring device |
| CN205978213U (en) * | 2016-07-25 | 2017-02-22 | 重庆长安汽车股份有限公司 | Coil spring underlay structure |
| CN205956275U (en) * | 2016-08-17 | 2017-02-15 | 诸暨市康宇弹簧有限公司 | Spiral spring |
| CN206889543U (en) * | 2017-07-07 | 2018-01-16 | 泰州市创新电子有限公司 | A kind of multilaminate coiled spring and its lifting support |
| CN208331072U (en) * | 2018-06-01 | 2019-01-04 | 博世电动工具（中国）有限公司 | Electric tool and its spring |
Also Published As
| Publication number | Publication date |
|---|---|
| CN108488285A (en) | 2018-09-04 |
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