CN104968478A - Wire cutter - Google Patents

Abstract

Provided is a lightweight wire cutter capable of cutting, with little force, a metal wire having a high degree of hardness, such as a hard wire. The hard wire cutter (1) comprises: a body section (2) which has a fixed blade (4) at the tip end; a movable section (12) which is supported by a main shaft (18) so as to be capable of pivoting relative to the body section (2); and an operating section (6) which is supported by an operating shaft (8) so as to be capable of pivoting relative to the body section (2). The movable section (12) is provided with a movable blade (14) in a position such that the movable blade (14) can contact or separate from the fixed blade (4). The operating section (6) is provided with a roller (10) which constitutes the point of action of a lever having the operating shaft (8) as the fulcrum. The roller (10) oscillates as a result of an opening/closing operation of an operating grip section (6a) of the operating section (6), and slides on a pressure receiving section (16) while exerting a pressing force on the movable section (12). A recessed section (16b) is formed in an intermediate sliding region of the pressure receiving section (16) on which the roller (10) slides.

Description

Wire rod cutter

Technical field

The present invention relates to a kind of handheld tool cutting off wire rod, especially, relate to a kind of wire rod cutter cutting off metal wire rod.

Background technology

As the handheld tool for cutting off wire rod, widely use scissors, pliers etc.But, in order to cut off the higher wire rod of the hardness such as metal wire, need to produce larger power when cutting off.Figure 8 illustrates the existing wire rod cutter easily cutting off metal wire by producing powerful power.

The wire rod cutter 100 of Fig. 8 opens by handle 101 and handle 102 instrument that shutoff operation cuts off wire rod, wherein, above-mentioned handle 101 has cutter portion 103 in front end, and above-mentioned handle 102 is installed on from this handle 101 in the dendritic front end 108a propping up spot film 108 extended in the mode that can freely rotate.This handle 102 is connected with the cutter portion 107 with cutter portion 104 by connecting rod piece 105.In addition, connecting rod piece 105 is connected with cutter portion 107 in the mode can slided in elongated hole 107a.

According to this structure, when opening shutoff operation to handle 101,102, can with the pin 106 of front end for axle relatively opens closedown cutter portion 103,104.That is, this wire rod cutter 100 can utilize double leverage to produce larger power, and this double leverage is made up of the leverage of the leverage in the cutter portion 107 being fulcrum by pin 106 and the handle 102 centered by the 108a of front end.Therefore, the thicker metal wire such as mild steel line can be cut off with less power.Such as Patent Document 1 discloses the wire rod cutter that Fig. 8 is such.

Prior art document

Patent document

Patent document 1: Japanese Patent Laid-Open 2003-225480 publication

Summary of the invention

Invent technical problem to be solved

But, according to above-mentioned existing wire rod cutter 100, mild steel line etc. can be cut off with smaller power, but lever is configured to two-stage, therefore, is large-scale, needs to operate with two hands.Therefore, in order to cut off needs rigid line more energetically, need the effect being configured to instrument more maximize to increase lever.Therefore, operability significantly reduces.

In addition, even if there will be a known a kind of small-sized as ratchet cutter, also can produce larger power to carry out the instrument split.But, in above-mentioned ratchet cutter, often cut off single line material, just need repeatedly to open shutoff operation, therefore, cause operating efficiency to reduce, also increase the fatigue of operator.

Therefore, the object of the present invention is to provide a kind of wire rod cutter of the metal wire higher by hardness such as one-handed performance cut-out rigid lines.

The technical scheme that technical solution problem adopts

To achieve these goals, the feature of wire rod cutter of the present invention comprises: main part, and this main part has dead knife and first control section; Operating portion, this operating portion utilizes the first axle to be supported on main part with the mode axle that can rotate, and there is second control section and service portion, wherein, closedown can be opened relative to first control section in above-mentioned second control section, and above-mentioned service portion carries out lever by the closedown of opening of this second control section centered by the first axle; And movable part, this movable part utilizes the second axle to be supported on main part with the mode axle that can rotate, and have in the position contacted with dead knife, be separated can moving knife, movable part is provided with compression zone, this compression zone from service portion be subject to making this can moving knife near the pressing force of dead knife, in addition, the slip zone line of the service portion on compression zone is formed with recess.

In addition, wire rod cutter of the present invention, on the basis of said structure, is characterized in that, in the mode making compression zone abut towards service portion, is exerted a force by movable part towards main part.

Invention effect

As mentioned above, according to the present invention, when carrying out rotating operation to second control section, service portion rotates because of leverage, is in the state pressed compression zone.Movable part rotates because of the pressing force of service portion, can moving knife near dead knife.In the recess in middle slip region being formed at compression zone, through the imaginary line of the first axle and service portion and compression zone angulation maximum.That is, sliding surface is less than other sliding area relative to the rotation direction angulation of the service portion of circular motion.Therefore, in recess, service portion is maximum for the chock reinforcement effect of compression zone, and the movement of the movable part produced because of the pressing of service portion is minimum.By this, powerful power can locally be produced.

In addition, according to the present invention, compression zone is biased to abut with service portion, and therefore, in the opening operation, shutoff operation of second control section, compression zone all contacts with service portion, thus can carry out the transmission of power efficiently.

Accompanying drawing explanation

Fig. 1 is the overall perspective view of the rigid line cutter of embodiment of the present invention.

Fig. 2 is the stereogram open state partly cut-away of the rigid line cutter of Fig. 1 represented.

Fig. 3 is the amplification stereogram of the movable part of the rigid line cutter of Fig. 1.

Fig. 4 is the action specification figure of the rigid line cutter of Fig. 1, Fig. 4 (a) be the figure representing full-gear, Fig. 4 (b) be the figure representing half-open position, Fig. 4 (c) is the figure representing full-shut position.

Fig. 5 is the schematic diagram representing the power relation worked between compression zone and roller.

Fig. 6 is the action specification figure specifically representing the power relation worked between compression zone and roller.

Fig. 7 represents the figure of cut-out power relative to the change of the opening size of the rigid line cutter of Fig. 1.

Fig. 8 is the figure representing existing wire rod cutter.

Detailed description of the invention

Accompanying drawing is used to represent the rigid line cutter (wire rod cutter) of embodiment of the present invention.

First, use Fig. 1 ~ Fig. 3 to be described structure, then, use Fig. 4 ~ Fig. 7 to be described action.

Fig. 1 is the stereogram of the entirety representing rigid line cutter 1.Roughly divide this rigid line cutter 1, this rigid line cutter 1 is made up of these three components of main part 2, movable part 12 and operating portion 6.In addition, Fig. 2 the periphery partial cutaway of the movable part 12 of main part 2 is come represent opening operation portion 6 state under rigid line cutter 1.In addition, Fig. 3 only amplifies expression movable part 12.

With reference to Fig. 1, be provided with main body handle part 2a (first control section) in the end side of main part 2, between the relative tabular component of another side, be fixed with dead knife 4 in sandwich-like.This dead knife 4 is installed and removed by bolted, even if there occurs turned etc., also can easily change.

Operating portion 6 has operation handle part 6a (second control section), and utilizes operating axis 8 (the first axle) to be supported on main part 2 with the mode axle that can rotate.By this, operate handle part 6a and can open closedown relative to main body handle part 2a.Herein, in conjunction with reference to Fig. 2, be provided with roller 10 across operating axis 8 and the opposite side operating handle part 6a, this roller 10 produces leverage by the operation of operation handle part 6a.In the present embodiment, in leverage, the state towards main part 2 curving is formed as the peripheral part of the roller 10 of fulcrum and application point.

The peripheral part of roller 10 is formed by relative tabular component.In addition, utilize above-mentioned relative tabular component to clamp main part 2 from outside, be supported on main part 2 to make operating portion 6 axle.In addition, the tabular component of main part 2 above-mentioned dead knife 4 being clamped into sandwich-like is formed with bending elongated hole 2b.The axle 10a being configured with roller 10 is run through in the mode can slided in this elongated hole 2b.

As shown in Figure 2, movable part 12 is formed by tabular component, and is supported to can rotates towards main part 2 with eccentric state by main shaft 18 (the second axle) axle.In addition, the position can contact with dead knife 4 in the spinning movement centered by main shaft 18, be separated is provided with can moving knife 14.In addition, be provided with compression zone 16 at the ora terminalis towards roller 10 side of operating portion 6, this compression zone 16 is subject to the pressing force produced from the leverage of roller 10.

By this, when compression zone 16 is subject to pressing force from roller 10, movable part 12 rotates, can moving knife 14 near dead knife 4.Herein, when with reference to Fig. 3, the known zone line for roller 10 slip at compression zone 16 is formed with recess 16b.In the present embodiment, compression zone 16 by main shaft 18 (in Fig. 3 for convenience of explanation and with chain-dotted line only substitution table axis is shown) centered by outside diameter be formed with outside diameter protuberance 16a, be formed with recess 16b at zone line, be formed with internal side diameter protuberance 16c at internal side diameter.In figure 3, the border of above-mentioned jog is indicated with chain-dotted line.In addition, between the internal side diameter protuberance 16c and main shaft 18 of compression zone 16, breach 12b is formed with.

Be back to Fig. 2, one end and this breach 12b of torsion spring 16 are locking.This torsion spring 26 is configured to using the operating axis 8 of the center of rotation as operating portion 6 as spring-loaded body, and towards making to exert a force to movable part 12 in the direction of opening, the interval of moving knife 14 and dead knife 4.That is, movable part 12 is biased compression zone 16 is abutted with roller 10.

Have employed said structure, therefore, when making operation handle part 6a near main body handle part 2a, the active force that roller 10 overcomes torsion spring 26 moves along compression zone 16 towards main shaft 18 side.By this, can moving knife 14 near dead knife 4, can wire rod be cut off.

Then, the action of Fig. 4 ~ Fig. 7 to rigid line cutter 1 is used to be described.

Fig. 4 shows three states of the aperture of operation handle part 6a.Wherein, Fig. 4 (a) shows full-gear, and Fig. 4 (b) shows half-open position, and Fig. 4 (c) shows full-shut position.

First, with reference to Fig. 4 (a), when operating handle part 6a and being in full-gear, roller 10 is in the state abutted with the outside diameter protuberance 16a (with reference to Fig. 3) near the top 12a in the compression zone 16 of movable part 12.

In the present embodiment, being defined as by the diameter of the wire rod that can be contained in the maximum gauge of the edge of a knife like this can the opening size of moving knife 14 and dead knife 4.In this Fig. 4 (a), the diameter of the imaginary wire rod of the size that imaginary circle 51 represents is 5.3mm, and therefore, opening size 52 is 5.3mm.To this, as the example cutting off object, illustrate the wire rod 50 of diameter 3.2mm.By this, under the state of Fig. 4 (a), wire rod 50 can moving knife 14 and dead knife 4 not clamped, and therefore, operation handle part 6a can not be subject to the cut-out resistance from wire rod 50, can rotate towards closing direction.

Fig. 4 (b) shows the half-open position that operation handle part 6a closes to centre position.As known in the figure, on the wire rod 50 cutting off object because of can moving knife 14 and dead knife 4 and be formed with local breach.In this condition, opening size 53 is about 2.0mm.That is, the cut-out resistance from wire rod 50 is subject to, the state that the rotation load being in operation handle part 6a is risen.

Now, the roller 10 abutted with compression zone 16 moves towards the mode that main shaft 18 side is close with the outside diameter protuberance 16a of the 12a side, top from movable part 12 (with reference to Fig. 3).The state of the continuous movement in the region that further there is illustrated the recess 16b (with reference to Fig. 3) being formed at centre position in the sliding area of the roller 10 on compression zone 16.

Fig. 4 (c) shows operation handle part 6a and closes completely, can contact with dead knife 4 by moving knife 14, the state that the cut-out of wire rod 50 terminates.Now, the recess 16b of the slip zone line of roller 10 from the compression zone 16 being formed at movable part 12 out moves to the position of the internal side diameter protuberance 16c (with reference to Fig. 3) be more formed at by main shaft 18 side.

Then, before concrete example illustrates the power acted between compression zone 16 and roller 10 and the relation of aperture operating handle part 6a, the relation of compression zone 16 and roller 10 is first schematically described in Figure 5.In addition, in conjunction with the structure of above-mentioned Fig. 2 with reference to periphery.In Figure 5, chain-dotted line 30 shows the radius vector direction abutment of compression zone 16 and roller 10 be connected with main shaft 18.In addition, chain-dotted line 31 is orthogonal with chain-dotted line 30, represents the direction of rotation of movable part 12.

Fig. 5 amplifies the part illustrating roller 10 and abut with compression zone 16.Roller 10 carries out circular motion centered by operating axis 8, but can replace to the chock carrying out rectilinear motion approx and consider.

Therefore, as shown in Figure 5, the roller 10 being carried out lever by operation handle part 6a is expressed as chock 28, and the lever revolving force worked in the circular arc direction along roller 10 is as the propulsive force of chock 28.

Like this, under the effect of the chock 28 based on lever revolving force 22, have vertical resistance 20 and act on compression zone 16 from the bearing surface of chock 28.But movable part 12 is supported by main shaft 18 axle, therefore, can only move up in the side of the chain-dotted line 31 representing direction of rotation.Therefore, movable part 12 is subject to chain-dotted line 31 durection component of vertical resistance 20 and the power of cam revolving force 24.Like this, relative to the bearing surface of compression zone 16 with roller 10, the circular motion direction angulation of roller 10 is less, then the reinforcement effect produced by chock 28 is just remarkable.

Then, as the concrete example of Fig. 5, use Fig. 6, be described with the power relation that the state of three shown in Fig. 4 acts between roller 10 and compression zone 16 accordingly.Fig. 6 represents the structure of the abutment portion of roller 10 and movable part 12, and Fig. 6 (a) shows the power relation of full-gear, and Fig. 6 (b) shows the power relation of half-open position, and Fig. 6 (c) shows the power relation of full-shut position.In addition, for convenience of explanation, in figure 6, eliminate the structure of the operating portion 6 beyond the main part 2 of covering movable part 12, roller 10, and schematically illustrate position relationship in order to the profile showing movable part 12 and roller 10.

From the state of Fig. 6 (a) to the state of Fig. 6 (c), show roller 10 on compression zone 16 from outside diameter towards the situation of internal diameter Slideslip.In addition, (in 6 (c), the lever revolving force 22 acting on roller 10 is shown with certain size at Fig. 6 (a) ~ figure.

First, with reference to Fig. 6 (a), under full-gear, roller 10 abuts with the outside diameter protuberance 16a (with reference to Fig. 3) near the top 12a of movable part 12.Now, significantly the tilting towards towards main shaft 18 side of the vertical resistance 20 that produces of the roller 10 pairs of lever revolving forces 22.Therefore, the cam revolving force 24 of the direction of rotation component (chain-dotted line 31 durection component) of movable part 12 is less.But the distance of abutment and main shaft 18 is the longest, therefore, even if larger wedge effect can not be obtained, also enough torques can be obtained.

Then, with reference to Fig. 6 (b), under half-open position, roller 10 with from outside diameter protuberance 16a towards the borderline region of recess 16b (reference Fig. 3) in compression zone 16 abut.Now, vertical resistance 20 towards different from the state of Fig. 6 (a), towards near movable part 12 direction of rotation towards working.Therefore, as being described in use Fig. 5, can obtain the reinforcement effect of chock, the size of the cam revolving force 24 of chain-dotted line 31 durection component sharply increases.In addition, be also enough with the distance of main shaft 18, therefore, can powerful torque be obtained, easily cut off.

Then, with reference to Fig. 6 (c), show under full-shut position, roller 10 is from recess 16b towards the state of internal side diameter protuberance 16c movement.Now, vertical resistance 20 towards identical with Fig. 6 (a), significantly tilt towards main shaft 18 side.But at the abutted position of roller 10, different from the situation of Fig. 6 (a), direction and compression zone 16 angulation of lever revolving force 22 are little.Therefore, can obtain the reinforcement effect of chock, the size of vertical resistance 20 is far longer than the situation of Fig. 6 (a).Therefore, fully can make up the torque reduction because abutted position produces near main shaft 18, therefore, the cutting action at the end of maintaining, can reliably fulfil assignment.

Then, about the operation of the rigid line cutter based on certain hold, the relation of cut-out power and opening size has been shown in the chart of Fig. 7.In addition, the figure of Fig. 7 to indicate as the rigid line cutter 1 of present embodiment the distinctive tendency that causes because being formed with the structure of recess at the slip zone line of compression zone, the not characteristic of the rigid line cutter 1 shown in Fig. 1 ~ Fig. 6 itself.

With reference to Fig. 7, when the side larger from opening size observes chart successively, along with opening size diminishes from larger side, cut-out power slowly increases.In addition, cut-out power sharply increases from a certain opening size.Then, when reducing opening size, cut-out power sharply reduces.

As mentioned above, rigid line cutter according to the present embodiment, can produce powerful power in the intermediateness of opening size, and can suppress less by cut-out power in cut-out initial stage and ending phase.

Owing to having above-mentioned feature, therefore, even if in metal wire rod, be also particularly suitable for cut-outs such as rigid lines higher for hardness.

That is, character more crisp when the metal wire that general hardness is higher has a ductility extremely low and moderate finite deformation.Therefore, when approach is larger, destroy at a certain position, and terminate along with fracture sharply to cut off.That is, when cutting off rigid line, without the need to producing cut-out power in the mode all covered in the region of gauge or diameter of wire, it is ideal for being configured to produce powerful power in the stage from incision till destruction produces.

In the rigid line cutter 1 of above-mentioned present embodiment, consider this point.Specifically, be designed in the stage in the early stage, roller 10 diminishes with the bearing surface of compression zone 16, and the velocity of rotation of movable part 12 becomes large.By this, do not contribute to can moving knife 14 or dead knife 4 arrive wire rod till cut-out region in, significantly can rotate with less power, this improves operating efficiency.

In addition, can, in stage of abutting with wire rod of moving knife 14 and dead knife 4, need cut-out power to be passed to wire rod quickly.Therefore, roller 10 is designed to be changed to the angle that can obtain maximum wedge effect with the abutment angle of compression zone 16.

Then, in cut-out ending phase, as mentioned above, cutting ongoing metal wire rod more crisp, without the need to larger power, therefore, inhibit cut-out power to relax reaction.By this, also can prevent dispersing of cut off machine, and operation can be carried out safely.

As mentioned above, rigid line cutter according to the present embodiment, the local, turned position needed for cut-out wire rod produces powerful cut-out power, and at the initial stage operating area being helpless to cut off, improves the velocity of rotation of movable part, thus can realize the raising of operating efficiency.In addition, cooperatively designing the region that can obtain wedge effect with the region needing most cut-out power, therefore, just can effectively cut off by means of only once holding operation.Powerful power can be produced as ratchet cutter etc., but when comparing with the instrument that shutoff operation repeatedly opened by needs, significantly can shorten the activity duration.

By this, even if utilize existing rigid line cutter to need two hands to carry out the rigid line etc. of the φ 3.2mm of operation, also can cut off with an one-handed performance like a cork.

In addition, in the above-described embodiment, exemplified with the service portion being applied leverage by operating portion 6 on the compression zone 16 of movable part 12 from outside diameter towards the structure of internal diameter Slideslip.But being not limited to this, also can be the structure from internal side diameter towards external diameter Slideslip.Such as, by configuring service portion between the fulcrum and force of operating portion, service portion from internal side diameter towards external diameter Slideslip, and with the reinforcement effect that can obtain chock towards formation compression zone, also can obtain identical effect.

In addition, in the above-described embodiment, the structure formed by recess 16b and the internal side diameter protuberance 16c of outside diameter protuberance 16a, slip zone line exemplified with compression zone 16, as long as but at least form recess at slip zone line.That is, formed compression zone with the tangent line angulation of the tangent line of point on the compression zone abutted with roller and the arc orbit of roller in the mode that slip zone line is minimum, then can obtain the reinforcement effect of chock when cutting off wire rod, and can easily cut off.

In addition, in the above-described embodiment, exemplified with arranging roller 10 using as the structure of service portion compression zone 16 being applied to pressing force, if but can slide at the recess 16b of compression zone 16, then also can be the such structure of such as sliding pin.

Industrial utilizability

Wire rod cutter of the present invention only produces the powerful cut-out power of the reinforcement effect based on chock in the pivot region needed for cutting off, and therefore, can improve operating efficiency, and can cut off wire rod by less power.Therefore, be useful as the rigid line cutter that metal wire higher for the hardness such as rigid line, piano wire is cut off.

Symbol description

1 rigid line cutter (wire rod cutter)

2 main parts

2a main body handle part (first control section)

2b elongated hole

4 dead knives

6 operating portions

6a operates handle part (second control section)

8 operating axis (the first axle)

10 rollers (service portion)

12 movable parts

12a top

12b breach

14 can moving knife

16 compression zones

16a outside diameter protuberance

16b recess

16c internal side diameter protuberance

18 main shafts (the second axle)

20 vertical resistances

22 lever revolving forces

24 cam revolving forces

Claims (2)

1. a wire rod cutter, is characterized in that, comprising:

Main part, this main part has dead knife and first control section;

Operating portion, this operating portion utilizes the first axle to be supported on described main part with the mode axle that can rotate, and there is second control section and service portion, wherein, closedown can be opened relative to described first control section in described second control section, and described service portion carries out lever by the closedown of opening of described second control section centered by described first axle; And

Movable part, this movable part utilizes the second axle to be supported on described main part with the mode axle that can rotate, and have in the position contacted with described dead knife, be separated can moving knife, described movable part is provided with compression zone, this compression zone from described service portion be subject to making described can moving knife near the pressing force of described dead knife, in addition, the slip zone line of the described service portion on described compression zone is formed with recess.

2. wire rod cutter as claimed in claim 1, is characterized in that,

In the mode making described compression zone abut towards described service portion, described movable part is exerted a force towards described main part.