RU2167964C1 - Heddle frame drive for heald machine - Google Patents

Abstract

FIELD: textile engineering. SUBSTANCE: drive has drive shaft mounted in drive casing and connected through kinematic transmission with main shaft of spinning machine, and planetary starting clutches, with number of clutches corresponding to number of heddle frames. Each planetary starting clutch cooperates with heddle frame through carrier, corona gear and pair of retainers mounted on rotary pins with programmable device and with leverage crank. Rotary pin of each corona gear retainer is fixed through bracket on beam rigidly secured to heddle frame drive casing and rotary pin of each carrier retainer is secured through its bracket on beam mounted for rocking relative to drive shaft pin. EFFECT: increased efficiency, wider operational capabilities and enhanced reliability in operation. 6 cl, 12 dwg

Description

 The invention relates to the field of textile machinery, and more particularly to a device for a lifting carriage of a loom.

 More than 85% of the assortment of fabrics produced in the world is produced on weaving looms by the method of weaving using heavy heald frames driven by cranks, cams or from a lifting carriage. The drive of the heald frames with cranks or cams is used only in the production of simple weave fabrics, having an advantage over the heald carriages in productivity. The market requires a solution to the problem of creating such a lifting carriage, which would cover the entire area of production of fabrics of simple and small-weave weaves.

 A known drive of the lifting frames of the lifting carriage, the idea of which was developed by the Stabley company (Switzerland), is Switzerland's head patent N 531073, D 03 C 5/00, 11/07/70, and patents EP 0446155 A, 09.91, USA 4924915, reflecting the development of the idea. 05/15/90. The drive contains a planetary type speed modulator at the input of movement from the main shaft of the weaving machine to the lifting carriage, the drive shaft and the cranks of the linkage gears mounted to it to the heald frames of the weaving machine. The drive also contains cranks installed between the drive shaft and the housing with clamps, not shown in these patents, controlled by a given program for weaving the fabric produced.

 The mechanical mode of action of the drive of the heald frames, implemented by Stoible in serial production, models the technology of producing fabric on an open-shed weaving machine, namely, the group of warp threads together with the heel-shaped frame remains stationary in the open shed for a whole number of weft laying cycles, or but moves in an open throat in order to change the position of the warp threads relative to the weft thread. In order to translate the specified mechanical method of forming an open pharynx on a weaving machine into the design of a lifting carriage, three bodies are used: an actively rotating drive shaft, a passively rotating crank with a lock and a drive housing. The strap frame is moved if the lock blocks the crank with the rotating drive shaft and remains stationary if the lock blocks the rotary crank with the drive housing. For the subsequent movement of the heald frame, the latch must unlock the fixed crank from the drive housing and re-lock it with a rotating drive shaft. The situations during the forward and return stroke of the lock are not identical from the point of view of assessing the initial mechanical state of the system, however, both situations, in order to exclude impacts at the moment of locking the rotating drive shaft or the fixed drive housing of the retainer frames, require reducing the drive shaft rotation speed to zero .

 The main disadvantage of the known drive is that deep modulation of the rotation speed of its drive shaft leads to irreparable loss of time in the phases of movement, and the locking of the heald frames in a fixed open pharynx causes a break in the cycles of their movement. In this drive, the basic requirement for rotary machines is not fully met, namely, there is no continuity of movement when performing basic technological operations: movement and locking of the heald frames in the open throat. Therefore, the known drive cannot be classified as rotational based only on a formal attribute - the cylindrical shape of its constituent parts. The specified disadvantage cannot be eliminated without changing the method of action of the structure.

 The disadvantages of the operating parameters of the known drive are a consequence of the imperfection of its circuit diagram.

 A high level of acceleration of the movement of the heald frames is determined by the zero initial conditions of their movement - heald frames begin to move from a state of rest, and the time of movement is limited by deep modulation of speed, and as a consequence of these reasons, the level of the calculated kinematic accelerations of the heald frames is more than twice physically achievable .

 The low speed mode of the known drive is associated with its overload by inertial forces, an increased level of vibration, parametrically excited speed modulations.

 The combination of the active (drive shaft) and passive (crank) organs in a pair reduces the controllability of the system, which led to the use of a shock drive for moving clamps, rigid springs to lock the lock frames in an open throat and rigid clamp stops in a well-known drive of the release frames. Another disadvantage of the known drive is the insignificant variation in the law of movement of the heald frames, especially in the direction of obtaining short dwell phases of the heald frames in the open throat, in connection with which, the well-known shaft-lifting carriages with speed modulator significantly (up to 50%) reduce the speed characteristics of modern shuttleless looms .

 A known drive of the heald frames of the rotational hedge carriage (RF patent N 2001169, 02.10.92, international application PCT / RU 93/00028, 04.02.93, international publication WO 94/08081, 04/14/94), containing a crank lever transmission to the heald frame, connected by a gear with a carrier of a planetary clutch mounted on a drive shaft of a lifting carriage and interacting with a crown wheel and carrier with a programming device by means of a pair of clamps mounted on the drive shaft with the possibility of rocking motion relative to its axis p means of cams. The drive shaft is installed with the possibility of unidirectional uniform rotation, and the planetary inclusion clutch is connected to the crank using a carrier. The locking of the carrier or the crown wheel of the planetary clutch is blocked by the simultaneous rotation of the carrier and the crown wheel and, accordingly, the swinging movements of both clamps.

 In the specified drive, the main feature of rotary machines is realized - locking and movement of the heald frames are carried out with continuous rotation of the drive shaft, carrier, crown wheel and their clamps, while the heald frame in the position of the open pharynx receives small movements that do not have a harmful effect on the weaving process. The locking of the planetary clutch locks is made without impact at the moment of rotation of the clamps relative to the axis of the drive shaft with maximum speed. Both bodies locked by the clamps: the crown wheel and the carrier are actively moving bodies that carry moment load, which provides increased controllability of the clutch. The latches after the initial push from the software device in the future move with the accompanying action of a planetary clutch on them.

 A low level of acceleration of the heald frames, close to the physical limit, is achieved due to the fact that at the initial moment of its movement the masses of the heald frames already have an initial speed, and the drive full cycle time is used to move the heald frames. Due to the transition to a fundamentally new drive scheme with a continuous rotational method of forming an open pharynx, it becomes possible to reduce the estimated inertial loads on the retainer frames by more than two times in comparison with the known shaft lifting carriages and thereby increase the life of the shed forming machine by 5 ... 6 times loom mechanism. The absence of speed modulation as a source of vibrational excitation, rigid kinematic locking of the heald frames in the open throat, the possibility of shockless control of the clamps, low load on the clamps - all this creates the conditions for stable control of the drive at operating frequencies of more than 1000 duck laying cycles per minute.

 The disadvantage of this drive is that the planetary clutch together with the cams performs simultaneously two most important functions, firstly, it provides shock-free execution of the program of movement and locking of the heald frames in accordance with the weaving pattern of the fabric produced on the loom and, secondly, sets the law movements of heald frames. The combination of two functions in one body makes it difficult to obtain optimal parameters for each function separately. For example, it is difficult to obtain the laws of motion of the heald frames with a long phase of standing in the open pharynx.

 In addition, the implementation of the swinging motion of the carrier clamps and the crown wheels at the same time complicates the design of the drive, while the rigidity of the installation of the crown wheel clamps located on a common movable axis that accepts the maximum loads from the moving frames in the open throat decreases.

 The purpose of the invention is the expansion of the technological capabilities of the drive of the heald frames through the use of cyclograms of their movement with a long phase of standing in the open throat, as well as improving the reliability of the drive design.

 This goal is achieved by the fact that in the known drive of the heald frames of the rotational hedge carriage, comprising a drive shaft connected by a kinematic transmission to the main shaft of the loom, installed in the body of the heald frame drive, on which planetary engagement clutches are installed, each interacting by means of a carrier, according to the number of heald frames, crown wheel and mounted on the rotation axes of a pair of clamps with a software device and with a crank lever transmission to the heald frame, its drive shaft is connected to the main the weaving shaft of the loom by means of a mechanism for correcting rotation speed, made in the form of a crank-rocker mechanism with a rotating link; the rotation axis of each clamp of the crown wheel by means of a bracket is mounted on a massive beam rigidly fastened to the drive housing of the heald frames, and the rotation axis of each clamp of the carrier by means of its bracket is fixed on a light beam having the possibility of oscillating motion relative to the axis of the drive shaft, while the planetary clutch of inclusion interpenetrating each other, the drive shaft is gear, the carrier is monolithically connected to the crank of the linkage to the heald frame and mounted on the drive the output shaft by means of a roller bearing and a splined sleeve, the crown wheel is freely seated on a ring with wedges separating the splined bushings and roller bearings of the drive of neighboring planetary couplings on the drive shaft, the satellites are equipped with damping rings and are located in the spaces between the wedges of the ring, the end surfaces of the carrier and rings with wedges are provided with annular grooves for placing balls in them, separating adjacent planetary couplings, compressed by the force of Belleville springs; clamps of the carrier and the crown wheel are interconnected by a three-arm control lever interacting with the software device; the rotation speed correction mechanism can be made in the form of non-circular gears (one of which can be round) or in the form of planetary mechanisms similar to known speed modulators with a maximum deviation of the rotation speed of the linkage crank to the heald frame relative to the average speed per cycle by no more than thirty%.

 The essence of the invention lies in the fact that the optimal kinematic laws of movement of the heald frames on modern shuttleless looms are close to the law created by the uniformly rotating crank, and to achieve the optimal laws of movement of the heald frames it is enough to make a small correction of the speed of rotation of the cranks. Impactless locking by the carrier clamps and the crown wheel of the planetary inclusion clutch is provided by vibrational rotation relative to the axis of the drive shaft of only the lightly loaded carrier clamp. The crown wheel retainer, which accepts the main load from the heald frames, is rigidly fixed with its axis to the drive housing.

 The planetary clutch provides software inclusion of the movement of the heald frame and its blocking with small displacements in the open pharynx, the rotation speed correction mechanism provides the optimal law of movement of the heald frames in the open pharynx. The choice of the law of movement of the heald frames is determined solely by the technological requirements for fabric production on the loom and is not limited to any additional conditions for ensuring the functioning of the drive mechanisms.

 The kinematic characteristics of two processes: small displacements of the heald frame in the open throat position and the movement of the heald frame when opening a new pharynx pass without breaking into each other, which leads to soft dynamic modes of the drive-heald frame system at high speeds of the loom.

 The present invention also discloses new layout solutions and the design of the most important drive mechanisms of the heald frames with functional features that make it possible to characterize it by its mode of action as rotational.

 In FIG. 1 shows a General view of the heald frames in the context of his body by a plane passing in the direction of the shafts and axes.

 In FIG. 2 - the head part of the drive shaft of the drive in an enlarged image scale.

 In FIG. 3 - the tail of the drive shaft of the drive in an enlarged image scale.

 In FIG. 4 - section of the drive plane perpendicular to its axes and shafts.

 In FIG. 5 is a rotation speed correction mechanism in the form of a crank-link mechanism with a rotating link when viewed from the side of the drive drive shaft in the direction of the link shaft.

 In FIG. 6 is a general view of the planetary inclusion clutch with a conditionally remote support of the crown wheel — rings with wedges.

 In FIG. 7 is a cross-sectional view of a planetary engagement clutch.

 In FIG. 8 is a three-dimensional image of a ring with wedges.

 In FIG. 9 is a general view of the drive of the heald frames in an embodiment with a rotation speed correction mechanism in the form of non-circular gears.

 In FIG. 10 - a mechanism for correcting rotation speed in the form of a pair of gears, of which one round is eccentrically offset relative to the axis of its rotation, and the opposite is non-circular.

 In FIG. 11 is a rotation speed correction mechanism in the form of a pair of non-circular gears.

 In FIG. 12 is a graph of changes in angular rotational speeds ω of the linkage crank to the heald frame, depending on changes in the rotation angles θ of the drive drive shaft.

 The drive of the heald frames of the rotational hedge carriage includes a drive shaft 1 connected by a kinematic transmission 2 to the main shaft of the loom, mounted rotationally in the drive body 3 and bearing a crank 4 of the crank mechanism (Fig. 5), connected by means of stone 5 to the rocker 6 made on the faceplate 7, mounted on the shaft 8. The shafts 1 and 8 are parallel and offset by the amount of eccentricity E shown in FIG. 5. The value of the relative eccentricity of the position of the axes of the mating shafts, determined by the ratio of the absolute values of the eccentricity E and radius Rb from the axis of rotation of the drive shaft 1 to the axis of the crank 4, does not exceed 0.4.

 A block of bevel gears is fixed on the shaft end opposite to the faceplate 7, of which the bevel gear 9 is connected to the drive shaft 11 by means of the bevel gear 10 and the bevel gear 12 is connected by means of gear 13, shaft 14, cams 15, rollers 16, rocker 17, shaft 1 and fixed on the shaft 18, a pair of levers 19 and associated links 20 with the rockers 21 of the light beam 22 (Fig. 4), carrying, using the brackets 23, the latches 24 drove 25 (Fig. 7) of the planetary clutch 26, shown separately in Fig. 6, 7, 8. Rocking chairs 21 are mounted on the drive shaft 11 by means of rolling bearings 27, 28, 29 and Belleville springs 30.

 The planetary clutch 26 includes a carrier 25, bearing a crank 31, axles 32 of the satellites 33, a bearing 34, a spline sleeve 35 for landing on the teeth of the drive shaft 11 and the connecting rod 36 with the bearing 37. On the carrier 25, holes 38 are made for engagement with the latch 24 (Fig. 4), as well as on its end surface, a groove 39 is made for placing balls 40 in it. A ring 42 with wedges 43 is pressed by means of balls 41 to the inner plane of carrier 25 by means of balls 41, which serves as a support of rotation for the crown wheel 44, linked by its gear with satellites 33 and made with holes 45 for engagement with the latch 46 (Fig. 1, 4). The satellite 33 contains a damping ring 47 made of synthetic material with the aim of balancing the loads between the satellites and damping the peak loads. Satellites 33 are installed in the space between the wedges 43 of the ring 42 and the inner plane of the carrier 25.

 Each planetary clutch 26 mounted on the drive shaft 11 by means of a spline sleeve 35, a roller bearing 34, thrust bearings 40, 41 and disk springs 30, is connected with a link gear 48 to the weaving mechanism of the weaving machine by its connecting rod 36, mounted rotationally on the crank 31, the drive lever 49 which is mounted rotationally on the axis 50.

 A massive beam 52 is fixed in the housing 3 with screws 51, bearing on itself the retainers 46 of the crown wheels 44, mounted rotatably on brackets 53, fixed with screws 54 on the massive beam 52.

 The planetary clutch 26 interacts with the holes 38, 45, respectively, the carrier 25 and the crown wheel 44 (Fig. 7), by means of the latches 24, 46 and the three-armed control lever 55 with the traction body 56 of the software device, while the latch 24 is pressed by the force of the spring 57 to the roller 58 of the lever management 55.

 In FIG. Figure 9 shows an arrangement of a drive with a lateral kinematic transmission to the main shaft of the loom. The drive comprises a drive wheel 59 on the drive shaft 1, offset from its axis of rotation by an eccentricity value E, coupled to a non-circular gear wheel 60 (FIG. 10) mounted on a shaft 61 supporting the cam 15 for driving the light beam 22 with the latches 24 drove 25 planetary couplings 26 and a gear wheel 62 for transmitting rotation by means of gear 63 to the drive shaft 11. Of the family of gear pairs in the drive of the lifting frames, only those with a relative eccentricity of a round wheel determined from wearing the absolute value of the eccentricity E to the diameter do of the pitch circle of the wheel does not exceed 0.2.

 In place of a pair of gears 59, 60, a pair of non-circular gears 64, 65 (FIG. 11) can be installed with the ratio of the maximum radius of the driving wheel 64 to the minimum radius of the driven wheel 65 within the range of 1.7.

 Drive heald frames works as follows.

 Rotation from the main shaft of the loom comes through a kinematic transmission 2 to the drive shaft 1 of the drive and then: from the bevel wheel 12 is transmitted to the cam 15, which informs the swinging movement of the shaft 18, levers 19 and rockers 21 with light beam 22 mounted on them with clamps 24 drove 25 planetary couplings 26; from the bevel wheel 9, the rotation enters the drive shaft 11 and, accordingly, planetary couplings 26 mounted on it.

 In the event that the traction body 56 fixes the right extreme turning position of the three-armed control lever 55, the roller 58 holds the latch 24 in the locked position of the hole 38 of the carrier 25, and the hole 45 of the crown wheel 44 is released by the lock 46 at that moment. The oscillating movement of the carrier 25 and together with it, the crank 31 causes rocking with a small amplitude of the linkage 48, the drive lever 49 and, accordingly, the heald frame in its upper or lower position. The rotation of the carrier 25, reaching maximum speed in the middle position of the movement of the latch 24, is planetary transmitted to the crown wheel 44, and at the moment corresponds to the instantaneous stop of the hole 45 of the latter relative to its fixed latch 46 - a necessary condition for shock-free locking.

 In the event that the traction body 56 fixes the left extreme turning position of the three-armed control lever 55, the latch 24 leaves the hole 38 of the carrier 25, and the latch 46 blocks the hole 45 of the crown wheel 44. The rotation of the main shaft of the loom, adjusted by the crank mechanism (Fig. . 1, 5) or non-circular gears (Fig. 9, 10, 11, 12), in accordance with the specified law of movement of the heald frames, enters the drive shaft 11, drove 25 with cranks 31, which drive the heald frames in the open pharynx . In the extreme positions of the heald frames, the angular speeds of rotation of the latches 24 and drove 25 are aligned, which ensures their subsequent shockless locking, after which the smooth deceleration by the moving latches 24 drove 25 leads to a smooth acceleration of the light crown wheels 44 and to block the heald frames in the extreme positions, accompanied by small displacements.

 Thus, the power circuit to the heald frames is constantly in motion with small or large amplitudes of displacement. The indicated modes of motion are strictly consistent by the condition of a smooth transition of their kinematic characteristics from one motion picture to another.

 The idea of a continuous rotational method of forming an open pharynx has been tested experimentally on a working prototype that has been tested in Russia and at the world's leading consumer firm of remise lifting carriages. Currently, on the basis of the material of the present invention, the development of a serial design of a new generation of a rotational lifting jack carriage has been completed.

Claims (6)

 1. The drive of the lifting frames of the lifting carriage, comprising a drive shaft mounted in the drive housing, connected by a kinematic transmission to the main shaft of the loom, on which planetary clutches are installed according to the number of lifting frames, each interacting by means of a carrier, a crown wheel and a pair of clamps mounted on the rotation axes with a software device and with a crank lever transmission to the heald frame, characterized in that the axis of rotation of each latch of the crown wheel through the bracket is fixed to the beam rigidly fastened to the housing actuator heald frames and the latch pivot axis through its carrier arm fastened to a beam having a possibility of rocking motion relative to the drive shaft axis.  2. The drive according to claim 1, characterized in that the planetary engagement clutches are mutually penetrating into each other, the drive shaft is gear, the carrier is seamlessly connected with the crank of the linkage to the heald frame and mounted on the drive shaft by means of a roller bearing and spline sleeve, the crown wheel it fits freely on a ring with wedges dividing spline bushings and roller bearings on adjacent drive planetary couplings on the drive shaft, satellites are equipped with damping rings and are located in the spaces between the wedges The rings, the end surfaces of the carrier and the rings with wedges are provided with annular grooves for placing balls in them, separating adjacent planetary couplings, compressed by the force of the springs.  3. The drive according to claim 1 or 2, characterized in that the drive shaft is connected to the main shaft of the loom by means of a rotation speed correction mechanism made in the form of a crank-rocker mechanism with a rotary link, the crank-rocker mechanism with a rotary link is made with a relative the eccentricity of the position of the axes of the mating shafts, determined by the ratio of the absolute value of the eccentricity to the radius of the crank, not exceeding 0.4.  4. The drive according to claim 1 or 2, characterized in that the drive shaft is connected to the main shaft of the loom through a speed correction mechanism made in the form of a pair of gears, one of which is non-circular, and the conjugate with it is made round with a relative eccentricity, determined by the ratio of the absolute value of the eccentricity of the displacement of the wheel axis relative to its axis of rotation to the diameter of its pitch circle, not exceeding 0.2.  5. The drive according to claim 1 or 2, characterized in that the drive shaft is connected to the main shaft of the loom through a speed correction mechanism made in the form of a pair of non-circular gears with a ratio of the maximum radius of the driving wheel to the minimum radius of the driven wheel, not exceeding 1.7.  6. The drive according to any one of paragraphs.1 to 5, characterized in that the clamps of the carrier and the crown wheel are interconnected by a three-arm control lever interacting with a software device.

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