CN1523147A

CN1523147A - Warp yarn tension detecting mechanism for loom

Info

Publication number: CN1523147A
Application number: CNA2003101245385A
Authority: CN
Inventors: 阿部慎也; 孝; 牧野功; 村上康孝
Original assignee: Toyoda Automatic Loom Works Ltd
Current assignee: Toyota Industries Corp
Priority date: 2003-02-19
Filing date: 2003-12-31
Publication date: 2004-08-25
Anticipated expiration: 2023-12-31
Also published as: EP1544338A2; CN1306088C; EP1544338A3; JP2004250817A

Abstract

Warp T sent out from a warp beam 11 is guided by first and second rollers 13 and 14. The second roller 14 is positively swung through motion of a crank mechanism 39. The first roller 13 is supported by a back bracket 15 through the intermediation of a support lever 21 and a pivot 17. A load cell 25 included by a detection arm 35 connected to the support lever 21 detects a load applied to the first roller 13 by the tension of the warp T.

Description

A kind of warp tension testing agency of loom

Invention field

The present invention relates to a kind of warp tension-detecting mechanism of loom.

Background technology

Warp produced a very factor of hightension fluctuation when the harness motion of warp (opening motion) was weaving.Restriction is very crucial through this fluctuation of line tension for obtaining high-quality woven fabric.Japan Patent 02-269841A discloses a kind of loom, and wherein the elastic force of tension spring is applied to the tension rail that supports tension roller rotationally, and the bootable warp of drawing from small beam of roller can be absorbed by the elastic force of tension spring through the fluctuation of line tension.The tension force of warp is detected by load transducer by tension roller.By small beam being rotated provide the rotating speed of the transmission motor of warp can be according to controlling that load transducer obtains through line tension detection information.

In the disclosed loom of Japan Patent 07-42046A, be delivered to detection with the loom running swing displacement of the loose warp bar of swing synchronously and detect roller through the tension force of line tension, guide the warp of drawing simultaneously from small beam.The transmission of the swing displacement of loose warp bar has absorbed the fluctuation through line tension.Detecting roller through line tension by tension force is detected by load transducer.By small beam being rotated provide the rotating speed of the transmission motor of warp can be according to controlling that load transducer obtains through line tension detection information.

In the disclosed loom structure of Japan Patent 02-269841A, utilize the elastic force of tension spring to absorb,, can realize that under the very low situation of line tension suitable tension fluctuation absorbs under high speed as long as loom is not operated through line tension.On the other hand, when loom was operated under high speed, the elongation of tension spring and contraction suitably servo-actuated were moved in shedding.That is, the fluctuation through line tension can not absorb with satisfactory way.

On the contrary, under the situation of the disclosed loom of Japan Patent 07-42046A, the fluctuation of its middle longitude tension force is to absorb by the warp tension that loosens that tension force detects roller, and the oscillating motion that tension force detects roller suitably servo-actuated is moved in shedding.That is, the fluctuation through line tension can satisfactory way absorb.On the other hand, when the tension force of warp was very low, the effect of inertia that tension force detects the motion of loosening warp tension of roller increased, can not be with high Precision Detection through line tension.When the accuracy of detection of line tension is not high, just can not carries the rotating speed of roller, and be difficult to make the level that reaches hope through line tension with high accuracy control.

Summary of the invention

The purpose of this invention is to provide a kind of warp tension-detecting mechanism, its fluctuation through line tension can be delivered to warp by the swing displacement with the loose warp bar and absorb, and has reduced the effect of inertia that loosens through line tension motion, can high Precision Detection through line tension.

According to the present invention, a kind of warp tension-detecting mechanism of loom is provided, wherein being delivered to warp from the tension fluctuation of the warp of drawing through axle by the swing displacement with the loose warp bar absorbs, wherein the running of the swing of loose warp bar and loom is synchronous, the tension force of warp detects by first roller of guiding warp, and the warp tension-detecting mechanism comprises:

Second roller is supported in described loose warp bar rotationally, and the bootable described warp T of described second roller can be delivered to warp with the swing displacement of described loose warp bar; With

Detectors of load can detect the tension force of described warp by the load that detection is applied to the supporting mechanism that supports first roller rotationally.

In the present invention, the tension force of warp is meant around total tension force of a large amount of warps that twine through axle.Load detector can detect the load of reflection through line tension by first roller.That is, the load that the inertia of the easing motion of second roller does not influence load detector detects, even the tension force of warp is little, also can carries out high-precision load and detect (promptly through line tension inspection side).Be absorbed through the fluctuation of line tension the warp tension that loosens by second roller.So even lower through line tension, loom is with high speed operation, absorb by satisfactory way through the fluctuation of line tension.

Description of drawings

Fig. 1 is the side view according to the warp tension-detecting mechanism of the first embodiment of the present invention;

Fig. 2 is the perspective view according to the major part of the warp tension-detecting mechanism of the first embodiment of the present invention;

Fig. 3 is respectively a enlarged side view according to the major part of the warp tension-detecting mechanism of the first embodiment of the present invention to Fig. 5;

Fig. 6 is the chart that shows torque fluctuations;

Fig. 7 is the side view of warp tension-detecting mechanism according to a second embodiment of the present invention;

Fig. 8 is the enlarged side view of the major part of warp tension-detecting mechanism according to a second embodiment of the present invention.

The specific embodiment

First embodiment

Introduce the first embodiment of the present invention referring now to accompanying drawing 1 to 5.

In Fig. 1, be subjected to transmitting the driving of motor 12 through axle 11.The guiding and the maintenance that are subjected to first roller 13 and second roller 14 from the warp T that draws through axle 11 are in contact with it.Along the mobile alignment of warp T, second roller 14 is positioned at the downstream of first roller 13.

In Fig. 1, solid line circle C1 represents the maximum coiling diameter through axle 11, and broken circle C2 represents the minimum coiling diameter through axle 11.Under the situation of minimum coiling diameter, all warps on axle 11 all use up.

The mobile alignment S11 of warp T shown in Figure 3 (mobile alignment between the axle 11 and first roller 13) is corresponding to the situation through the coiling diameter maximum of axle 11.The mobile alignment S12 of warp T shown in Figure 3 (mobile alignment between the axle 11 and first roller 13) is the situation of median corresponding to the coiling diameter through axle 11.The mobile alignment S13 of warp T shown in Figure 3 (mobile alignment between the axle 11 and first roller 13) is corresponding to the situation through the coiling diameter minimum of axle 11.

As shown in Figure 2, tail-

bracket

15,16 is fixed to right and left side frame (not shown).As shown in Figure 1,

pivot

17 and 18 is supported in tail-bracket 15 with cantilevered fashion.As shown in Figure 2,

pivot

19,20 is supported in tail-bracket 16 with cantilevered

fashion.Support bar

21 and 22 is supported in

pivot

17,19 respectively rotationally.Loose

warp bar

23,24 is supported in

pivot

18 and 20 respectively rotationally and also can swings.First roller 13 is supported in the roller shaft 131 (in Fig. 1, left-hand side is corresponding to the rear end, and right-hand side is corresponding to front end) of

support bar

21 and 22 rear ends rotationally.Second roller 14 is supported in the roller shaft 141 at

loose warp bar

23,24 middle parts.First roller 13 can rotate around roller shaft 131, and second roller 14 can rotate around roller shaft 141.The mobile alignment S2 and the S3 that represent along chain-dotted line Fig. 1 from the warp T that draws through axle 11 move.

Be connected to the fore-end of

support bar

21,22 by the pin connected mode that comprises

pivot pin

27,28 and

bar

29,30 as the

load transducer

25,26 of load detector.In addition,

load transducer

25,26 is connected respectively to tail-

bracket

15,16 by the pin connected mode that comprises

pivot pin

31,32 and bar 33,34.Load transducer 25 and

bar

29,33 constitute detection arm 35, comprise as its a part of load detector.Load transducer 26 and

bar

30,34 constitute detection arm 36, comprise as its a part of load detector.

Support bar

21 and 22,

pivot

17 and 19, and tail-

bracket

15 and 16 has constituted the supporting mechanism that supports first roller 13.The position in

pivot

17 and 19 axle center 171,191 is the position of the fulcrum that support the

support bar

21,22 of first roller 13 rotationally.The position in the axle center 132 of roller shaft 131 is link positions of the roller shaft 131 of the

support bar

21,22 and first roller 13.This link position is the power application point of support bar 21 and 22.First roller 13 is arranged on the following and back of second roller 14.The position of the fulcrum of support bar 21,22 (position in

pivot

17 and 19 axle center 171,191) is arranged to be not less than the height and position in the axle center 132 of first roller 13, and is not higher than the height and position in the axle center 142 of second roller 14, and is positioned at the front of second roller 14.

The

detection arm

35,36 that comprises

load transducer

25 and 26 is connected to support

bar

21 and 22, intersects (seeing Fig. 3 and 4) with line L, and line L connects the fulcrum and the point of application, as what can see along the roller shaft 131 of first roller 13 axial.The angle of cut of support bar 21 and detection arm 35 be by

pivot pin

27 and 31 centers line K1 (see figure 3) with along the L shaped angle of cut γ that becomes of the axial appreciable line of roller shaft 131.The angle of cut of support bar 22 and detection arm 36 be by

pivot pin

28 and 32 centers line K2 (see figure 5) with along the L shaped angle of cut γ that becomes of the axial appreciable line of roller shaft 131.In this embodiment, angle of cut γ is the right angle.

Coiling diameter through axle 11 changes to minimum diameter from maximum gauge, and maximum gauge represents with solid line circle C1, and minimum diameter with dashed lines C2 represents, as shown in Figure 1.Be independent of the variation of this winding angle, warp T is arranged to greater than the second angle beta (see figure 4) in the L shaped first angle [alpha] (see figure 4) that becomes of mobile alignment between the axle 11 and first roller 13 and intersection, and second angle becomes by the mobile alignment S2 of warp T between first roller 13 and second roller 14 and intersection are L shaped.

Load transducer

25,26 is arranged on second angle beta, one side less than first angle [alpha], as what see along the roller shaft 131 of first roller 13 axial.Be that

load transducer

25,26 is arranged on the

support bar

21,22.

Loose warp bar

23,24 is connected to crank mechanism 39 movably by release lever 37,38.Crank mechanism 39 rotates synchronously with the running of loom, makes the tension force cyclic fluctuation of

loose warp bar

23,24 when the swing of

pivot

18,20 meets the loom rotation.That is, the loose warp bar of swinging between solid line position shown in Figure 3 and solid line position shown in Figure 4 by rotatablely moving of crank mechanism 39 23,24 is synchronous with the running of loom.Second roller 14 moves forward and backward by the periodic wobble of

loose warp bar

23,24, and is synchronous through the cyclic fluctuation of line tension during the swing of

loose warp bar

23,24 and loom rotate a circle.Therefore absorbed by the swing of second roller 14 through the cyclic fluctuation of line tension during loom rotates a circle.

The part that the tension force of warp T is applied to the load of first roller 13 is received by

load transducer

25,26 by support bar 21,22.

Load transducer

25,26 detects the fractional load that receives by support bar 21 and 22.Be the tension force that load that

load transducer

25,26 detects has reflected warp

T.Load transducer

25,26 detected load informations are delivered to control computer 10.Computer 10 relatively reflects target load and load transducer 25, the 26 detected load that preset goal tension, and the rotating speed of control transmission motor 12 makes the load of detection consistent with target load then.That is, control computer 10 can be controlled the rotating speed of transmission motor 12, makes that to detect the warp T tension force of load corresponding to

load transducer

25,26 consistent with goal tension.

First embodiment has following advantage.

1-1. can detect load by the reflection warp T tension force of first roller 13 as the

load transducer

25,26 of load detector.Be not delivered to first roller 13 with the swing displacement of the synchronous

loose warp bar

23,24 of loom running but be delivered to second roller 14.That is, the inertia of the easing motion of second roller 14 does not have influence on the load detection of load transducer 25,26.Therefore, even the tension force of warp is lower, also can high accuracy carry out detecting through line tension.Be absorbed through the fluctuation of the line tension easing motion by roller 14, so can satisfactory way absorb through the fluctuation of line tension, even the tension force of warp T is lower, loom is to run up.

Understand minimizing 1-2. twine the diameter through axle 11 of warp T when weaving, the contact angle θ 1 (seeing Fig. 3 and Fig. 4) of the warp T and first roller 13 changes thereupon.But the contact angle θ of the warp T and second roller 14 2 does not change, and feasible vary in diameter through axle 11 can not absorb to the tension fluctuation that is undertaken by the easing motion of second roller 14 in negative effect.

1-3.

detection arm

35,36 is connected to support

bar

21,22, can intersect with line L, line L connects the fulcrum of

support bar

21,22 and the power application point of

support bar

21,22, as the axial finding along the roller shaft 131 of first roller 13.The link position of

detection arm

35,36 and support bar 21,22 (be pivot 17 with 19 position) has constituted the application point of relative position of the fulcrum.The tension force of warp T arrives

load transducer

25,26 with the moment form around the position of the fulcrum of

support bar

21,22.

Among Fig. 5, arrow R0, R1, R2 and R3 represent the tension force of warp T.Each tension force R0, R1, the value of R2 and R3 equates mutually.Tension force R1 is corresponding to the situation through the coiling diameter maximum of axle 11, and promptly the mobile alignment of warp T is S11.Tension force R2 is the situation of median corresponding to the coiling diameter through axle 11, and promptly the mobile alignment of warp T is S12.Tension force R3 is minimum situation corresponding to the coiling diameter through axle 11, and promptly the mobile alignment of warp T is S13.

Among Fig. 5, arrow Q1 represents making a concerted effort of tension force R0 and R1, and arrow Q2 represents making a concerted effort of tension force R0 and R2, and arrow Q3 represents making a concerted effort of tension force R0 and R3.Q1, Q2 and Q3 act on first roller 13 with joint efforts, and pass through the axle center 132 of roller shaft 131.In this embodiment, the make a concerted effort position of Q1, Q2 and Q3 departs from the position of the fulcrum (that is the axle center 171 and 191 of pivot 17,19) of

support bar

21,22.

In Fig. 6, curve E representative make a concerted effort Q1, Q2 and Q3 and apart from Z1, the variation of the product of Z2 and Z3, power Q1, Q2 and Q3 change with the variation through the coiling diameter of axle 11; Z1, Z2 and Z3 represent the distance between the axle center 171 and 191 of arrow that these are made a concerted effort and

pivot

17 and 19, so curve E is the variation of moment.In the example shown, moment M2 minimum, at this moment coiling diameter r2 in the middle of the coiling diameter of axle 11 is.When the coiling diameter through axle 11 was minimum diameter r1, moment M1 was maximum.Moment M3 is the moment when the coiling diameter of axle 11 is maximum gauge r3, and it is slightly smaller than maximum moment M1.Be moment M1, M2, the relation of M3 is M1＞M3＞M2.

In this embodiment, the moment shown in the curve E among Fig. 6 changes the determining of position of the position, support bar 21 of roller shaft 141 of position, second roller 14 of the roller shaft 131 cause

first roller

13 and 22 pivot 17,19.Promptly, by setting roller shaft 131, roller shaft 141 and

pivot

17,19 position, make the mobile alignment S11 of warp T, S12, L shaped first angle [alpha] that becomes of S13 and line is greater than second angle beta, and second angle beta becomes by the mobile alignment S2 of warp T and line are L shaped, and moment is tended to change by the mode of curve E.

Suppose

support bar

21,22

pivot

17,19 position upwards changes, and is α＞β to keep the pass between first angle [alpha] and second angle beta, identical with shown in the example of the position relation between center of rotation 111, roller shaft 131 and the roller shaft 141 of axle 11.Thereafter, moment is tended to change shown in the curve G1 of Fig. 6.The position of supposing the

pivot

17,19 of

support bar

21,22 changes downwards, is α＞β to keep the pass between first angle [alpha] and second angle beta.Thereafter, the moment tendency changes shown in curve G2 among Fig. 6.That is, corresponding to the coiling diameter of the minimum of a value of curve G1 less than coiling diameter r2, corresponding to the coiling diameter of the minimum of a value of curve G2 greater than coiling diameter r2.Corresponding to coiling diameter r1 to the moment change amount of the curve G1 of the variation of r3 and G2 moment greater than curve E.

When the moment that occurs shown in curve E changes, through the coiling diameter of the axle 11 moment change amount when maximum gauge r3 changes to minimum diameter r1 very near minimum of a value.That is the very approaching detected minimum of a value when line tension does not change of detected error, through line tension.The result is, utilizes the tension force of inspection side that the rotating speed control of transmission motor 12 can high accuracy be carried out, thus can provide hope through line tension.

Usually, at first definite center of rotation (axle center 142 of roller shaft 141) through the center of rotation 111 of axle 11, the center of rotation of first roller 13 (axle center 132 of roller shaft 131), second roller 14.When the axle center 132 of determining roller shaft 131, during the axle center 142 of roller shaft 141, determine the mobile alignment of the warp T between first roller 13 and second roller 14.In addition, to determine in advance through the maximum gauge and the minimum diameter of axle 11, so, when the axle center 132 determined through the center of rotation 111 of axle 11 and roller shaft 131, also determine the mobile alignment of the warp T between the axle 11 and first roller 13.Therefore, change, determine the center of rotation (

pivot

17 and 19 axle center 171,191) of

support bar

21,22 at last for obtaining the moment shown in the curve E.In this embodiment, the determining of the position of roller shaft 131, roller shaft 141 and

pivot

17,19 can realize that the moment of the curve E that introduces above changes, that is, and and moment minimum during coiling diameter in the middle of the coiling diameter through axle 11 is.

Second embodiment

Below, will be introduced second embodiment with reference to figure 7 and Fig. 8.Wherein with first embodiment in identical parts represent with identical mark.

Shaft-like counterweight 40 horizontal expansions, and be supported in the leading section of support bar 21,22.Counterweight 40 is arranged to be parallel to the roller shaft 131 of first roller 13.Counterweight 40,

support bar

21,22 and roller shaft 131 form rectangular frame.

Counterweight 40 is used to prevent roller shaft 131 and

support bar

21,22 distortions that link to each other.In addition, counterweight 40 can make counterweight and be supported in weight balancing between first roller 13 of

pivot

17,19, prevents that the weight of first roller 13 and roller shaft 131 is applied to load transducer 25 and 26.Such weight balancing can reduce the The Effect of Inertia Force of first roller 13.

For the present invention, the following examples can also be arranged.

(1) among first and second embodiment that introduce in the above, the pass that can also set between first angle [alpha] and second angle beta is α＜β, and

load transducer

25 and 26 is set to the first angle [alpha] side.Be that

load transducer

25 and 26 can be arranged to be lower than

support bar

21 and 22.

(2) can also first roller be arranged on the downstream of second roller along the mobile alignment of warp.

(3) can also adopt such structure, wherein load transducer only is arranged on the side in tail-

bracket

15 and 16 both sides.Like this, a bar by the no-load sensor in the

detection arm

35 and 36 among the embodiment shown in Fig. 1 to 4 constitutes.

(4) detection arm 35 can be other angles except that the right angle with 36 with the L shaped angle that becomes of intersection.

Introduce in detail as top institute, according to the present invention, proposed a kind of structure, it can loosen warp tension by the roller of guiding warp, reduces the effect of inertia of easing motion.Therefore, can high accuracy carry out detecting through line tension.

Claims

1. the warp tension-detecting mechanism of a loom, wherein from the tension fluctuation of the warp thread T that draws through axle (11) by with loose warp bar (23,24) swing displacement is delivered to warp and absorbs, the swing of wherein said loose warp bar and the running of loom are synchronous, the tension force of described warp detects by first roller (13) of guiding warp, it is characterized in that described warp tension-detecting mechanism comprises:

Second roller (14) is supported in described loose warp bar (23,24) rotationally, and the bootable described warp T of described second roller can be delivered to warp with the swing displacement of described loose warp bar; With

Load transducer (25,26) can detect the tension force of described warp by the load that detection is applied to the supporting mechanism (15,16,17,19,21,22) that supports described first roller (13) rotationally.

2. warp tension-detecting mechanism according to claim 1 is characterized in that, described second roller (14) is set to along the downstream of described first roller (13) of the mobile alignment of described warp T.

3. warp tension-detecting mechanism according to claim 2, it is characterized in that, described first roller (13) is supported in rotating support bar (21 rotationally, 22), comprise detectors of load (25,26) detection arm (35,36) be connected to described support bar, connect described support bar (21 along axially can seeing of described first roller (13), 22) position of the fulcrum (171,191) and the intersection L in the axle center (132) of the above first roller (13) of described support bar, warp mobile alignment between described intersection L and described small beam (11) and described first roller (13) forms first angle [alpha], second angle beta is formed by the warp mobile alignment between described intersection L and described first roller (13) and described second roller (14), first angle [alpha] is different with second angle beta, described load detector (25,26) is arranged on the less side of angle in described first angle [alpha] and described second angle beta.

4. warp tension-detecting mechanism according to claim 3 is characterized in that, described second angle beta is less than described first angle [alpha].

5. according to claim 3 or 4 described warp tension-detecting mechanisms, it is characterized in that, is the center with the position of the fulcrum (171,191) of described support bar (21,22), and counterweight (40) is connected to the support bar of described first roller (13) opposite side.