JPS58104245A - Load reducing apparatus of drive mechanism of constitutional parts alternately reciprocated between both end positions in loom - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a device for reducing the load on a drive mechanism for a component that reciprocates between end positions in a loom.

The reciprocating components in the use of such a device in a weaving machine include a rigid grid AA- for inserting the weft thread and a reed for driving the inserted weft thread. In each case, the component must be moved from one end position to the other end position and then returned again to the starting position in the shortest possible time. A mass corresponding to κ is then accelerated and then braked again. This is clearly seen when driving the reed. In the case of a loom, the driving force of the continuously rotating main drive shaft is taken by the eccentric force ▲ or the crank κ.

In this case, modern weaving machines usually use complementary double eccentric devices, which operate with sufficient clearance. Significant stresses are exerted by these eccentric devices, and these stresses are transferred via roller levers directly to the rocking parts, such as the reed, κ,′! Or, depending on the case, it is transmitted through an intermediate member. From the perspective of improving the desired performance of the loom.

This problem κ is given an important meaning. If for some reason,
An increase in the operating speed leads to an increase in stresses, which leads to larger dimensions and an increase in the mass to be moved because of the load capacity of the components.

However, it is not only the high stress values achieved that are problematic, but also the acceleration and deceleration forces that lead to undesired rotational unevenness, which not only leads to vibrations and rocking of the loom. , the condition of reaching high load peaks during operation is seen as a drawback.

Therefore, the object underlying the present invention is to reduce to the greatest extent the stresses which are applied from a continuous rotary drive, for example from an eccentric device, and which have to be transmitted to the oscillating components, thereby making the above-mentioned drawbacks possible. The goal is to manufacture equipment that prevents as much damage as possible. According to the invention, the solution to this problem is provided with elements on at least one rocking component that are elastically deflectable in both directions of movement, in which case these elements
It acts on a connection point fixed to the machine and is essentially in a relaxed position at the central position of the swinging component. Can be fired! Various components can be used as tatami slips. For example, mechanical or pneumatic springs can be used.

It is obvious that the spring element can be pretensioned in one direction or in the other direction or in both directions. It is not necessary from the essence of the invention that the resilient element exhibits its relaxed state exactly at the center of the structural part to which it is fixed, but rather that the relaxed state of the spring is more or less offset from the geometric center position. Can be adjusted. At that time.

It is also possible to use a resilient element with a spring characteristic that varies along the movement path.

The resilient element can be placed on any reciprocating component of the drive mechanism. For example, it can be arranged on the reel itself or on a roller lever capturing the movement of the eccentric and, if necessary, on a rocking interposer provided. In both cases, the springing element is fully tensioned at one end of the component and becomes more and more relaxed with the start of the rocking movement until it reaches a zero-order state approximately at the midpoint of the movement stroke. , in the second part of the motor stroke.

The springing element is tensioned in the opposite direction (taking up all or at least part of the deceleration stress to be applied). Then, in the final phase of the rocking movement, the deceleration stress to be applied is not primarily provided by the drive eccentric disc, but is at least partially caused by the elastic added by the originating element.

According to the invention, a substantial reduction in the applied beam stress;
Hence energy savings in output balance.

The operation of Klk planes in line can be made quieter. Dimensioning the spring element such that the energy absorbed by the spring force and stored at each end of the rocking motion essentially corresponds to the accelerating or decelerating stress occurring at the beginning or end of the rocking motion. is desirable. In this way, in the ideal case,
11. Desires that occur as a result of acceleration or deceleration stresses applied during operation of the loom. <It is difficult to remove rotational unevenness. Furthermore, during the rocking movement, different magnitudes of acceleration and deceleration are desirable in the area of the end position.

Therefore, it is clear that the present invention can be used and adapted to the case of carp having different lightness inversion times and even resting times.

Furthermore, even when known mass-balancing weights are used in this type of weaving machine, acceleration and deceleration stresses can be reduced or even substantially eliminated by the measures of the invention. Furthermore, the invention allows a rapid movement of components, such as reeds, even when the loom is started from a standstill, thereby preventing the risk of start-up scratches in the woven fabric.

Fundamentally, the invention provides, by virtue of the arrangement of its non-element relative to the oscillating component, in all driven devices in which a reciprocating oscillating movement is introduced from a continuous rotary drive, for example in a crank drive. It can be used to reduce the burden. The spring systems may be arranged one at a time, or several at a time if necessary. For example, the drive system may be divided into several eccentric discs or double eccentric discs, each with one spring system or the like. Can be placed at both ends of the reed shaft.

A few embodiments of the present invention will be described below with reference to Appendix 8JK.

As an example of a reciprocating component in a loom.

The drive device for the weft thread searching Gritspano R- was selected and is shown in FIG. In this figure, only the most important components are shown. Seven frames or a part of the housing of the textile machine is schematically indicated by 1. On the continuously rotating drive shaft 2, two eccentric discs 3 as a double eccentric device are mounted, the force faces of these discs being contacted by one roller 4 in each case. These rollers 4 are oscillated by two arms, and A-
The swing levers 5 are movable around a swing bearing 6 and are connected to the ear segment Leno e-7. Swing lever 5 and gas segment lever A=7
The eccentric disk 40 performs a reciprocating rocking motion according to the force plane.Y) Both end positions of the swinging of the lever 7 are shown by chain lines on both sides of the intermediate position. 4 Yasegure A,
The ear rim placed on -7 is the driven gear 8, wooden
From this driven ear 8, the reciprocating movement is transmitted to the drive pinion 9 via a gearing system which is not shown in detail.

This part engages part 1 of the grit/arm part 10 shown in cross section. As shown in FIG.
This is converted into forward/backward movement of the bale in the direction perpendicular to the plane of the figure 0. To that extent, this construction corresponds to the state of the art mentioned in the text TjRK, in which all the stresses for the rocking must be applied from the eccentric device.

By the way, in this case, the load on the drive mechanism is reduced by installing a spring system, which has two tension/spring systems.
It consists of compression springs 12m and 12b, both of these springs are connected to the gear segment Le/? -7 at a fixed point 11 or otherwise secured. The other ends of the springs 12m and 12b are respectively fixed to fixed points on the loom in opposite directions from the fixed point 11. In this case, the tension of each of the springs 121 and 12b can be adjusted using the adjustment screw 13 as necessary.

Both springs 12m and 12b have one swing gas segment
Depending on the direction of movement of 9-7, its fixed point 1 on the rocking structure
It works from 1. /? The threaded stems 12a, 12b are in an equilibrium or untensioned state in the central position shown. A movement in either of the two oscillation directions results in a spring tension in the spring system, which tension is maintained until a return oscillation of the ear segment 7 in the opposite direction begins, which Once started, the stored energy acts in concert, thereby achieving at least a partial relief of the drive eccentric, both in the case of acceleration and in the case of braking of the rocking part.

The initial tension of the spring can be varied not only symmetrically (but also asymmetrically), and in this way other forms of stress distribution can be selected as required ('Seyer Segment Reper 7 A state of relaxation equilibrium can be created at other positions f.Therefore, the energy storage will have different values in the direction of true motion.This may have important significance depending on the circumstances, e.g. In the case of a dalipper, this is when a short reversal time or a long reversal time or a stationary time is desired at one end position compared to the other end position.Also, different spring characteristics are shown in the opposite direction of movement. If springs are used, a corresponding action is obtained.

As a supplementary note, there is a large degree of freedom in the construction of the structure. It can also be placed on top of.

In another embodiment, a reed drive mechanism is chosen for FIG. 2, again using a mechanical spring system for load relief. Instead of the tension/pressure spring system shown in FIG. 1, a coil spring is provided in this case. The main drive shaft is the same (indicated by 2, and the two eccentric discs mounted thereon are indicated by 3). In addition to the possible intermediate position of the receptacle 15, its end positions on both sides are shown in chain lines.

A swinging arm 16 is provided opposite to the reed 15, and a coil spring is freely connected to this arm via a rad 1f. The coil spring 18 is fixed to the loom housing IK at a fixed point 19. This structure is preferably such that the coil nose 18 is in a relaxed state at the center of the reed 15, as shown in FIG. The operation of this structure is similar to that of the first embodiment of the arrangement, so there is no need for special explanation.

Moreover, various modifications are possible in this embodiment. For example, spring characteristics can be changed. This is because by moving the fixed point 19 of the coil spring 18, the page effective length of the coil spring is changed. It is also possible to use paddle spring bundles (instead of one coil spring in each case) and in this case also the properties of the spring bundles can be changed. Different spring characteristics in one direction or the other or even varying spring characteristics along the travel path are possible.

Also, the tensioning system of the spring system can be adapted to the structural needs. in each case between the reciprocating rocking structure of the drive mechanism and the fixed connection point of the loom.

It is important to have a bidirectionally acting spring connection.

It is obvious that within the scope of the gist of the present invention, the above-mentioned spring systems may be mutually exchanged with Kt' or changed to other spring systems. It is possible to change to a torsion panel system such as a spiral spring. In some cases, the rotating shaft 1 of the reciprocating component
For example, it is also possible to use a torsion rod connected to the fabric winding shaft.

In the structure described in FIG. 3, the gripper par lO
An air spring system is used to reduce the load on the drive mechanism. At the front end of the gripper 10, gratings are shown. As in FIG. 1 above, a gripper par 10 with stomach teeth engages a reciprocating drive pinion 9. The rear end of the gripper par 10 runs protected in a tube 21. Such structures are known per se.

In this case, according to the present invention, in order to reduce the burden on the drive machine, a piston n is arranged at the rear end of the gripper par 10, and this piston slides in the tube to guide the trailing edge of the gripper par 10. . The tube sections 23J1 to 23b on one side or the other side of the piston, or both tube sections 23J1 to 23b, are constructed as compressed air chambers and are closed off or sealed, for example as in the front passage of the grits arm 10. ing. The closed cylinders in the tube sections 23m to 23b act as a pneumatic spring system and serve to at least partially relieve the drive mechanism. In this case, a continuous alternation occurs between tension on one side, intermediate relaxation and tension again on the other side, in which case the energy dissipated during braking and stored accelerates Sometimes they work together again.

The above-mentioned modifications are also possible in the case of pneumatic spring systems. Similar to the characteristics of the mechanical spring system, the cylinder part 23
It is possible to adjust the air action of the thorn and 23b. In this case, a displacement container δ is provided at one end or the other end of the cylinder as required. In that case, the displacement container not only acts due to its volume (the element that causes the squeezing action,
For example, these containers can also be equipped with adjustable valves. Another possibility is cylinder g 23 a
(F) The rear wall is configured to be removable or movable as shown by the chain line in FIG. Thereby, the damping effect at the retracted end position of the gripper par can be changed.

According to another feature of the invention, it is also possible to selectively provide through holes or slits in the tube wall.

In that case, the air spring is deactivated in that area and its action is limited to the desired area.

If necessary, these through holes can be covered, so that the active area of the pneumatic spring system can be adapted to the respective needs. By using any one or a combination of these features of the present invention, it is possible to control the drive mechanism in a different manner to reduce the burden on the drive mechanism at one end position or the other end position of the grid/tano - If it is necessary to switch to strokes of different lengths, suitable adjustments can be made.

[Brief explanation of the drawing]

Figure 1 shows a weft thread insertion grid equipped with a mechanical triggering system.
The drive mechanism of the arm parr, FIG. 2 shows the arm circumferential drive mechanism with another mechanical springing system, and FIG. 3 shows the drive mechanism of the gripper par with a pneumatic springing system. 3... Eccentric disc, 7... Ear segment lever. lO... Gripper, 11... Spring fixing point, 12
m, 12b...Spring, 13...Adjustment screw, 14.
... Winding shaft, 15... Reed. 18... Coil spring, 19... Spring fixing point, 21
···tube. U...Piston, 23 heat, 23b...cylinder display,
25...Volume pump, 26...Valve. Applicant's agent Kiyoshi InomataFig, 2 Fig, 3

Claims (1)

[Claims] 1. For at least one swinging component, 1 is provided with flexible elements that can spring back, for example in the direction of angular movement, and in this case these elements are provided with respect to a fixed connection point of the machine. What is claimed is: 1. A device for reducing the burden on a drive mechanism of a component reciprocating alternately between two end positions in a loom, characterized in that the swinging component is in a tensioned state at its essentially central position; 2. The load-reducing device according to claim 1, wherein the spring characteristics of the resilient elements acting in opposite directions of movement are different. 3. Dimensioning the resilient element such that the energy absorbed by the resilient element and stored at the end position of the rocking motion essentially corresponds to the accelerating or decelerating stress occurring at the beginning or end of the rocking motion. A burden reducing device according to claim 1 or 2, characterized in that: 4. The load-reducing device according to any one of items 1 to 3 of the requirements for special requirements, characterized in that it uses an elastic element with spring characteristics that vary along the movement path. 5. The load-reducing device according to any one of claims 1 to 4, in which the pretension can be adjusted in the direction of angular movement in the resilient element. 6. The swinging component is provided with tension or compression springs acting in both directions of movement, and these springs are connected to the loom at the other end. The burden reduction device according to any of paragraph 5. 7. The load-reducing device according to claim 6, characterized in that an adjustment device is provided at the spring fixing position. 8. The coil panel according to any one of claims 1 to 5, comprising a coil panel fixedly stretched over the loom and freely connected to the swinging component at its free end. Burden reduction device. 9. The load-reducing device according to claim 8]1, characterized in that the working length of the coil spring is adjustable at its tensioned location. 10. The load-reducing device according to any one of claims 1 to 5, characterized by a torsion panel system connected to the rotating shaft of the swinging component. 11. A bill reduction device comprising a torsion rod connected to an i1 rotating shaft. 12. The load-reducing device according to any one of claims 1 to 11, which is used for driving a reed. 13. The load-reducing device according to any one of claims 1 to 7, characterized in that it is used in a swinging gas segment for driving a rigid grinder.
'149! Second bullet fired! 5. The load reduction device according to any one of items 1 to 5, characterized in that the cumulative value is M. 15. The load-reducing device according to claim 14, characterized in that it comprises a volumetric capacity connected to the pneumatic spring element via an adjustable valve. 16, comprising a rigid gripper which is guided through the tube, pushed out of the tube and returned into the tube, said gripper being guided in the tube by a piston at its rear end, said tube having at least one of said tube pistons; Claim ts14., characterized in that it is configured as a compressed air cylinder on the side. ! The burden reduction device according to either JI or Clause 15.