EP0613968A1 - Cam gearing with selective switching of a constant and variable course of an output shaft - Google Patents

Abstract

To produce terry and / or smooth fabric, a cam mechanism was created, consisting of a first and a second four-bar mechanism (43, 44), each four-bar mechanism being operatively connected to a roller lever (15) controlled by an eccentric (7). Both four-bar gears (43, 44) work on the reed shaft (46 ') of the weaving machine. A corresponding control and engagement mechanism (54) makes it possible to switch from one four-link mechanism to the other four-link mechanism. The cam mechanism is therefore suitable for the production of smooth and terry fabrics. <IMAGE>

Description

The invention relates to a cam mechanism with a selectively switchable constant and variable stroke of an output shaft, in particular for weaving machines for the production of terry and / or smooth fabrics according to the preamble of claim 1.

With terry weaving machines, gearboxes are required that accomplish two different movements. Different angles of rotation of the weaving shafts must be possible; about a position for forming a partial stop (formation of the pile height by the warp threads) and a position for a full stop of the reed.

A known weaving machine with a gear suitable for this purpose is shown, for example, in EP application 0 350 446. The various reed positions are achieved with this known arrangement according to the principle of the folding drawer. These are several articulated levers. One of the articulated levers is supported on an eccentric package which is non-rotatably coupled to the main drive shaft. The position of the reed to a roller lever is influenced by a toggle lever, this toggle lever being designed to be adjustable by means of a corresponding adjustment drive. In this way, the lever transmission ratio of the folding drawer can be made adjustable in the direction of the reed. When using a gear mechanism that works together with an articulated drawer, there is the disadvantage that the kinematic system as a whole is too soft, ie the pivot points cannot always be reached in a reproducible manner be, which is associated with a certain inaccuracy of the pivoting movement of the sley in the pile formation. The drive for the sley, which can be adjusted and adjusted via a spindle, has the disadvantage that it cannot cope with high speeds of the drive shaft, because rapid successive adjustment movements are required.

By using several interlocking toggle levers, there is the disadvantage of a high mass inertia thereof, which likewise does not allow high speeds. The inertia of the toggle lever mechanism also has an adverse effect on the wear behavior of the bearing points of the mechanism.

The object of the invention is therefore to provide a cam mechanism with a selectively switchable constant and variable stroke of the transmission output shaft. The gear should be particularly suitable for unprotected weaving machines for the production of terry and / or smooth fabrics, and it should ensure defined pivoting angles, in particular at high machine speeds, for the sley connected to the gear output shaft.

To achieve the object, the invention is characterized by the technical features set out in claim 1.

An essential feature of the invention is a cam mechanism with two independently operating four-bar drives, one of which is adjustable, while the other is not adjustable. A clutch device can be engaged between the two four-bar drives, which, depending on the switching position of a control device arranged on the main drive shaft, ensures that either only one four-bar drive or only the other four-bar drive acts on the transmission output shaft.

Thus, with regard to the use of the cam mechanism for defenseless weaving machines, there is the essential advantage that the aforementioned articulated levers (articulated drawer principle), which are associated with the disadvantages mentioned, are avoided, and that instead, exact pivoting angles of the weave drawer can be achieved.

The clutch device is connected to an engagement mechanism, which in turn can be brought into engagement with a control device on the main drive shaft, which consists of a control cam unit.

The design of the one four-bar drive as an adjustable gear has the advantage that at the beginning of the weaving process the required pile height can be set on the four-bar drive by a simple adjustment process using a rotation angle or stroke adjustment device.

The other four-bar drive is not adjustable because this is not necessary. Instead of providing a four-bar linkage for this purpose, in another embodiment of the invention it is possible to use a four-wheel drive, e.g. is formed from individual segments with interlocking.

The oscillating movement of the roller lever, which is connected to the main drive shaft, is transmitted to the shutter shaft.

As a coupling device, which selectively engages the adjustable four-bar drive arranged on the left-hand side or the non-adjustable four-bar drive arranged on the right-hand side, a toothed clutch acting in the axial direction is preferably used. It is a sliding shaft, one at its two free ends corresponding external teeth. The sliding shaft can be moved in the axial direction from a first to a second end position.
If the sliding shaft is in the left-hand end position, for example, then the right-hand toothing of the sliding shaft is disengaged from the four-bar drive arranged there on the right-hand side. The roller lever and the left-hand four-bar linkage are then in meshing engagement with the external toothing of the sliding shaft.

If the sliding shaft is in the right end position, the toothing of the roller lever and that of the left four-bar linkage are disengaged because the toothing on the right side of the sliding shaft is in engagement with the toothing of the roller lever on the right side. Depending on the position of the sliding shaft, the roller lever then transmits the oscillating movement either to the left-hand or right-hand four-bar lever of the four-bar drive and from there to the weaving shaft. The transmission takes place e.g. in a ratio of 3: 1 pile formation (partial stop) to full stop of the reed.

With the arrangement described there is the essential advantage that a simple adjustment drive for the sliding shaft can be provided, which essentially consists of a pair of pivot levers which is provided with a roller at the free ends, which roller on assigned control cams of the control device arranged on the main drive shaft rolls off. An exact transmission of the rotary movement of the main drive shaft via the control cams to the swivel levers is thus achieved, so that an exact, practically backlash-free transmission of the adjustment movement to the sliding shaft takes place. Such an adjustment drive can therefore be an exact adjustment even at higher speeds Manage the sliding shaft.

The four-bar drives used within the cam drive are low-mass. At high speeds you can achieve the exact angle of rotation of the shaft of the shutter, which is determined for the pile formation, and thus an exact swivel position of the reed.

It is important in the present invention that the cam mechanism described is not only suitable for a terry cloth function, but also for a smooth fabric function.

Two separate four-bar drives are provided for both operating functions, which can be switched alternately and alternately via the sliding shaft described.

If the gearbox is only required for a smooth fabric, then it is sufficient to use a single four-bar linkage, for which protection is also claimed. The sliding shaft is therefore not required in the formation of the cam mechanism for a smooth fabric. The transmission function is then as follows:
An eccentric package is flanged to the main drive shaft, which gives an oscillating movement to a roller lever. This roller lever is coupled to a four-bar linkage, which in turn is connected to the shaft of the shutter.

The succession of an eccentric set with a roller lever and a four-link drive connected downstream is claimed as essential to the invention for a plain-weave gear.

If, on the other hand, a terry cloth gear function is to be achieved in addition to the smooth fabric gear function, then it is essential to the invention that, starting from an eccentric package, the same roller lever is driven in an oscillating manner, and that, however, two four-bar drives are attached to the output of the roller lever, which alternate via an axially displaceable sliding shaft can be brought into engagement with the roller lever, each four-bar linkage in turn being connected to the reed shaft.

Fig. 1

den Schnitt durch ein Frottiergewebe-Getriebe gemäß der horizontalen Linie I-I in Fig. 2,

Fig. 2

eine Ansicht des Kurvengetriebes in Pfeilrichtung II gemäß Fig. 1,

Fig. 3

eine Ansicht des Verstellantriebes in Pfeilrichtung III gemäß Fig. 1,

Fig. 4

die Verbindung zwischen Schiebewelle und Einrückmechanismus als Einzelheit "X" gemäß Fig. 1,

Fig. 5

Mittel zur Drehwinkel- bzw. Hubeinstellung der Webladenwelle am linksseitigen Viergelenkhebel und die Arretierung der die Drehwinkelverstellung bewirkenden Mittel als Einzelheit "Y" gemäß Fig. 1,

Fig. 6

die Schiebewelle in der Rollenhebel-Hohlwelle integriert als Einzelheit "Z" gem. Fig. 1.

The invention is explained in more detail below using an exemplary embodiment. Further features and advantages of the invention which are essential to the invention emerge from the drawings and their description.
Show it:

Fig. 1

the section through a terry cloth gear according to the horizontal line II in Fig. 2,

Fig. 2

2 shows a view of the cam mechanism in the direction of arrow II according to FIG. 1,

Fig. 3

2 shows a view of the adjustment drive in the direction of arrow III according to FIG. 1,

Fig. 4

the connection between the sliding shaft and engaging mechanism as detail "X" according to FIG. 1,

Fig. 5

Means for adjusting the angle of rotation or stroke of the shutter shaft on the left-hand four-bar lever and locking the means causing the angle of rotation adjustment as a detail "Y" according to FIG. 1,

Fig. 6

the sliding shaft in the roller lever hollow shaft integrated as detail "Z" acc. Fig. 1.

A main drive shaft 3 is rotatably mounted in a gear housing 4, which is closed off on the right-hand side by a housing cover 29. A clutch-brake combination 1a is indicated on the main drive 1. There is also a reversing motor 2, which acts on the main drive shaft 3 if necessary.

The main drive shaft 3 is led out from the right side of the housing 4 in the form of a connecting shaft 5 and passes through a machine wall 6.

On the main drive shaft 3, an eccentric packet 7 is flanged, which consists of an eccentric 8 and an eccentric 9 (see also FIG. 2).
The individual eccentrics 8, 9 are combined by means of screws 10 to form an eccentric package. The eccentric package is non-rotatably connected to the main drive shaft 3.

An associated roller 11 or 12 of a roller lever 15 rolls on the outer circumference of each eccentric 8, 9. The rollers 11, 12 are connected to the roller lever 15 via associated roller bolts 13, 14. The roller lever 15 consists essentially of two identical arms 16, 17. The arm 16 is assigned the roller 12, the arm 17 is assigned the roller 11 and a middle arm 18 receives a free end of the roller bolts 13, 14 carrying the rollers 11, 12.

The roller lever 15 is rotatably received in associated bearings 52 in the gear housing 4, see also FIG. 6.
The coupling function of the left-hand four-bar drive is now shown in more detail.
It is essential here that the roller lever 15 itself has an internal toothing 20a, 21a, or is connected to the roller lever 15 by means of screws 20a ', 21a' with a machine element 20,21 having an internal toothing.

In alignment with the internal toothing 20a, there is a further internal toothing 24b of the four-bar linkage 24, which can also be formed by a gearwheel with internal toothing. The gearwheel is fastened to the four-bar lever 24 with screws 20b '. These two toothings 20a, 24b can be brought into meshing engagement with an external toothing 19c of a sliding shaft 19.

On the opposite side of the sliding shaft 19, the same machine elements equipped with toothings for the four-bar drive there are arranged.

In the position shown in Fig. 1, the left-hand toothing is engaged, i.e. the roller lever 15 is connected to the four-bar linkage responsible for producing the terry fabric, while on the right-hand side the toothing 21a of the roller lever 15 is disengaged from the associated external toothing of the sliding shaft 19.

The toothings 20a, 24b and the toothings 21a, 25b are each separated from one another by a play 22, 23, so that the assigned parts can be driven independently of one another, see also FIG. 6.

6, the oscillating roller lever 15 drives the four-bar lever 24, which is coupled to a pivot bearing 37, via the toothings 20a, 24b, 19c which are in engagement with one another. It is important that this pivot bearing 37 is adjustable. For this purpose, the area of the four-bar lever 24 below the pivot axis is designed as a fork-shaped arm 24a. The arm 24a has an arcuate guide 24c for the pivot bearing 37 for adjusting the stroke or angle of rotation of the output shaft 45 or 46.

The pivot bearing 41 is received between the arms 25a of the four-bar lever 25.

As can be seen from the description of the invention to date, the sliding shaft 19 jointly performs an oscillating movement derived from the eccentric package 7 due to its positive connection to the roller lever 15. It is important that this movement is not transmitted to the engagement mechanism 54. 4, the sliding shaft 19 and the connecting rod 26 are connected to one another in such a way that a play 55 is maintained between the end face 19a of the sliding shaft 19 and the end face 26a of the connecting rod 26. The two end faces are essentially sliding against each other.
The connection of the sliding shaft 19 and the connecting rod 26 takes place by means of a machine element 56 designed in the manner of a union nut, which on the one hand engages the shoulder 26c of the connecting rod 26 and on the other hand is connected to the sliding shaft 19 via a thread 19b.

According to FIG. 2, one end of a coupling 38 attaches to the pivot bearing 37 and is coupled to a further four-bar lever 43 via a pivot bearing 42. This lever is rotatably connected to the output shaft 45 by means of screws. The output shaft 45 is rotatably supported in the gear housing 4 according to FIG. 1.

The right four-bar drive consists essentially of the same parts, only with the difference that the pivot bearing 41 is not arranged to be adjustable. Otherwise, this swivel bearing connects one end of the coupling 40, which is coupled to a further four-bar lever 44, which in turn is connected to the output shaft 45.

1 and 3, the engagement mechanism 54 for the axial adjustment of the sliding shaft 19 consists essentially of a pair of pivot levers, a roller 32 being arranged at the respective free end of the respective pivot lever 30, 31. The respective roller 32 is in engagement with a control cam 33a of a control device 33 which is fixedly connected to the main drive shaft 3. There is only one swivel lever 30 or 31 with its roller 32 in engagement with the associated control cam 33a. This optional intervention is achieved by a pneumatic cylinder 35, which actuates a pivot lever 30, 31 via a pull rod 34.

Instead of the pneumatic cylinders 35 used, other actuators can also be used, e.g. Electromagnets, hydraulic or electromotive actuators.

Depending on the engagement of the pivot lever 30 or 31 with the main drive shaft 3, a pivoting movement is thus communicated to the shaft 28 to which the pivot levers 30, 31 are articulated.
The shaft 28 is rotatably connected to a lever 36, on the free and pivotable end of a pivot bearing 27 is arranged.
An operating lever 36 is pivotally attached to the pivot bearing 37.

One end of the actuating lever 36 is connected to the pivot bearing 27, while the same pivot bearing 27 on the other side connects the free end of the connecting rod 26, which is arranged on the sliding shaft 19. Depending on the position of the swivel levers 30, 31, the sliding shaft 19 is shifted oscillating in the axial direction in a ratio of, for example, 3: 1 (pile formation to full stop of the reed) into one end position or into the other end position.

As already shown above, FIGS. 1 and 6 show the left shift position of the sliding shaft 19. Here, the pivot lever 30 with the roller 32 is in engagement with the control cam 33a of the control device 33 arranged on the main drive shaft 3.

2, the same parts are provided with the same reference numerals. It can be seen that a very compact structure is achieved, the levers used defining exact pivot points.

In particular, it is important that, starting from the eccentric package 7, a roller lever 15 is used which, owing to the cam-controlled sliding shaft 19, alternates between one and the other four-bar drive (in the use of the gear as terry cloth gear) or only on a four-bar drive (in the use of the gear) as a smooth fabric gear) works.

It is therefore a change gear that can be switched via the sliding shaft 19 in a gear for the production of terry cloth or in a gear for the production of smooth fabric.

In Fig. 2 it can also be seen that the weaving shaft 46 is connected to a reed support 47, which in turn is connected to the reed 49,49 'via a blade strip 48,48'.
In a manner known per se, the heald frames 50 are arranged parallel to the reed 49. 2 shows two different pivot positions of the reed 49, 49 '.

Fig. 5 shows an actuator 57, consisting of a motor drive 57a and one on the motor shaft 57b in the direction of the double arrow 58, but non-rotatably arranged pinion 57c. The motor 57a is flanged to the outside of the gear housing 4.
According to FIG. 2, the pinion 57c can come in meshing engagement with the toothing 59a of a segment 59 rotatably connected to the four-bar lever 24.

To lock a stroke or rotation angle adjustment, the fork-shaped arm 24a according to FIG. 5 is connected to a locking device 60 which clamps the pivot bearing 37 between the inner side surfaces of the arms 24a. The locking device consists of a piston-cylinder unit 61 operated by pressure medium, the cylinder 61a of which is arranged on the side of the arm 24a lying parallel to the inner wall of the transmission housing 4. A piston rod 61c is connected to the piston 61b and extends through the bottom of the cylinder 61a, the arms 24a of the four-bar linkage 24 and the pivot bearing 37 of the coupling 38. The free end of the piston rod 61c is connected to a connecting element 62 designed as an abutment on the outside of the arm 24a pointing into the transmission interior.
After the stroke adjustment process, the cylinder space 61a 'is acted upon by pressure medium via a connection 63, thus locking the pivot bearing 37 between the arms 24a. The pressure medium is supplied via the connection 64 provided on the four-bar lever 24 and the channel 65 integrated in the four-bar lever 24, the connection 66 to the connection 63. Hydraulic control means which ensure the supply of the pressure medium and the locking are generally known and are not shown here.

At this point it should be pointed out again that the essence of the invention consists in the complex cam gear and that the cam gear is suitable from two switchable four-bar drives for realizing a terry cloth and a smooth fabric gear function.

Claims (18)

Cam gear with optionally switchable constant and variable stroke of an output shaft (45), in particular for weaving machines for the production of terry cloth and / or smooth fabric, wherein the elements transmitting the movement sequence of the output shaft (45), such as eccentrics (8, 9), are pivotally mounted Roller levers (15) and handlebars (24, 38, 43) and (25, 40, 44) are integrated between a motor-driven drive shaft (3) and the output shaft (45), the eccentrics (8 , 9) are arranged, with the circumferential contour of the scanning elements (11, 12) of the roller lever (15) in operative connection, with the link mechanisms (24, 38, 40) and (25, 40, 44) formed between the roller lever (15) and the output shaft (45) are integrated and with a switching device (54) connecting the articulated mechanisms with the roller lever (15), characterized in that that the articulated mechanisms are designed as four-bar gears and that the cam mechanism consists of at least a first and a second four-bar gear, - That in each case a four-bar lever (24, 25) is arranged coaxially to an imaginary pivot axis of the roller lever (15) on both sides and at a distance from the roller lever (15) in the housing (4), - That the four-bar mechanism can alternatively or alternately be brought into operative connection with the roller lever (15) by means of an engagement mechanism (54), - That the imaginary pivot axis of the roller lever (15) of a roller lever hollow shaft (15a) is enclosed, and that the roller lever hollow shaft (15a) has driver elements (20, 21) at its free ends, - That the roller lever hollow shaft (15a) is penetrated by a sliding shaft (19) which is alternatively or alternately in operative connection with the driving elements (20, 21) of the hollow shaft (15a), - That the sliding shaft (19) is coupled to the engaging mechanism (54) executing a switching movement, - That the engagement mechanism (54) is operatively connected to a control device (33) arranged on the drive shaft (3), - That the four-bar lever (24) has provisions (24c, 57, 59) for adjusting the angle of rotation of the shutter shaft (46), which serve to determine the pile height in the fabric and - That the pile height-determining four-bar lever (24) has a device (60) for locking the arrangements causing the rotation angle adjustment (24c, 57, 59). Cam mechanism according to claim 1, characterized by the design as a change gear, which can be switched between a pile fabric gear and a smooth fabric gear via the sliding shaft (19) axially adjustable by the control device (33) and the engagement mechanism (54). Cam mechanism according to claim 1, characterized in that each four-bar mechanism consists of the first four-bar lever (24) and second four-bar lever (25) arranged on the left-hand side and the right-hand side on the roller lever (15). Cam mechanism according to claim 1, characterized in that each of the driving elements (20, 21) arranged on both sides of the roller lever hollow shaft (15a) has an internal toothing (20a, 21a). Cam mechanism according to claim 4, characterized in that the driving elements (20, 21) are part of the roller lever hollow shaft (15a). Cam mechanism according to claim 4, characterized in that the entrainment elements (20, 21) are internal gears. Cam mechanism according to claims 1 to 3, characterized in that the first and second four-bar levers (24, 25), which are spaced apart from each driving element (20, 21), are pivotably mounted. Cam gear according to claim 7, characterized in that the first and second four-bar levers (24, 25) and the roller lever (15) can be pivoted about the imaginary axis and are laterally spaced in the gear housing (4) from the roller lever hollow shaft (15a). Cam mechanism according to one of claims 1 to 8, characterized in that the axis of the four-bar lever (24) is partially and the axis of the four-bar lever (25) completely as a hollow shaft and both axes have an internal toothing (24b or 25b). Cam mechanism according to claim 9, characterized in that the internal toothing (24b or 25b) of the four-bar linkage (24 or 25) can alternatively or alternately be brought into engagement with a corresponding external toothing (19c) of the sliding shaft (19). Cam mechanism according to claim 1, characterized in that the one free end of the sliding shaft (19) is positively connected to a connecting rod (26) of the engagement mechanism (54). Cam mechanism according to claim 1, characterized in that the engagement mechanism (54) consists of a connecting rod (26), a lever (36) which engages at the free end of the connecting rod (26) and which is rotatably mounted in a partial gear housing (29) (28) is preferably clamp-connected and consists of a pair of externally controlled pivot levers (30, 31) fixedly connected to the shaft (28). Cam mechanism according to claim 12, characterized in that each pivot lever (30, 31) carries at its free end a roller (32) which engages with one of the control cams (33a) of the control device (33) which is arranged on the drive shaft (3) in a rotationally fixed manner is feasible. Cam mechanism according to claim 12, characterized in that each pivot lever (30, 31) is connected to an actuator (35). Cam mechanism according to claim 1, according to which the precautions consist in the fact that one of the first two four-bar levers (24, 25), whose pivot axis is identical to the imaginary pivot axis of the roller lever (15), has a segment (59) provided with teeth (59a) , the teeth of which engage a disengageable pinion (57c) driven by an actuator (57) and the four-bar lever (24) has an arcuate guide (24c) for a pivot bearing (37) below its pivot axis, which has a coupling (38 ) connects the cam mechanism with the four-bar lever (24) with variable stroke. Cam mechanism according to claim 1, characterized in that the first four-bar levers (24, 25) have a fork-shaped arm (24a, 25a) for receiving a pivot bearing (37, 41). Cam mechanism according to claim 1, characterized in that the locking device (60) consists of a pressure-operated piston-cylinder unit (61), the cylinder (60a) of which is attached to one of the arms (24a), while the piston (61b) of which is a piston rod (61c ) which extends through the base of the cylinder (60a), the arms (24a) and the pivot bearing (37), at the free end of which receives a connecting element (62) which is designed as an adjustable abutment and which is supported on one of the arms (24a) . Cam mechanism according to claim 17, characterized in that the locking device (60) is provided in the region of the fork-shaped arm (24a).

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