• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    Shuttle embroidery machine with mass balance for at least one oscillatingly driven pivot shaft (11), the pivot drive is derived from a rotationally driven, rotating kingshell (1), wherein the mass balance is formed by at least one balancing mass (26) eccentric to the center of rotation of the pivot shaft with the pivot shaft (11) is connected.
    公开号:CH711529A2
    申请号:CH01052/16
    申请日:2016-08-15
    公开日:2017-03-15
    发明作者:Friedrich Gerardo；Ulmann Andreas；Wiegand Boris
    申请人:Saurer Ag；
    IPC主号:
    专利说明:

    The invention relates to a shuttle embroidery machine with mass compensation of the oscillating waves according to the preamble of claim 1.
    A mass balancing first order is only known in embroidery machines according to DE 19 724 425 A1, which have a fitted with movable embroidery needles embroidery head, the needle drives are each connected to a parallel to the longitudinal carriers carried by the embroidery machine driven main shaft ,
    For complete mass balance of such embroidery machine, it is known that the drive arrangement of the embroidery head each arranged on the driven main shaft, externally toothed gear and arranged on a parallel to the main shaft balancing shaft arranged second externally toothed gear, wherein the with their external teeth interlocking gears for complete compensation caused by the taking place in the vertical plane longitudinal movement of the needle bar and occurring in the horizontal direction transverse to the main shaft vibrations are each provided with a leveling compound.
    Disadvantage of the known embroidery machine is that it is not a shuttle embroidery machine, but an embroidery machine with an embroidery head, which is characterized in that a rotating rotary drive is present, which is comparable to a revolving crankshaft drive in an internal combustion engine.
    In such rotating rotary actuators, it is known from the aforementioned DE 19 724 425 A1 to perform a complete balancing first order, in which the oscillating mass of the drive connecting rod is compensated by a balancing mass on the outer circumference of the first drive shaft and thereby caused imbalance by a counterbalanced in the mass balanced second wave is compensated.
    Apart from the considerable effort in the arrangement of a counter-rotating, mass-balanced second wave is a completely different drive principle as compared to a shuttle embroidery machine, which have a completely different vibration behavior.
    This also applies to a drive for a stitch pattern means on a sewing machine according to DE 3 341 444 C2.
    The mass balance of rotating waves in general is also known, for example, from US 4 966 042 A1, where also the mass balance is to take place on a rotating shaft in the same sense, but this is not transferable to oscillating waves of a shuttle embroidery machine.
    1. problem statement (problem to be solved)
    At an industrial shuttle embroidery machine up to a thousand needles are simultaneously engraved in a cloth wall, whereupon a Hinterfadenschiff passes through the loop of the needle thread to hold the stitch / stitches on the fabric wall. The movement of the needles is straight.
    The motor drive this movement is originally, originating from an electric motor, circular. In order to obtain a translation from the rotation of the motor, a pivoting movement is derived via a gear, which is attached to a uniform circumferential king shaft. Naturally, this pivotal movement causes an imbalance which fundamentally causes the machine to vibrate. When the circulation number increases, it eventually comes, depending on the stimulating frequency, to resonant phenomena. These cause noises, inaccuracies and can even lead to the destruction of components.
    2. State of the art (previous technical status)
    So far, the frequencies of the resulting pivoting movements, which 1: 1 represents the number of stitches of the needles, in moderate areas.The excitation of the machine components is noticeable and audible, but has not yet led to resonant areas of the machine structure or the drive train.
    The translational movement is not compensated in all known embroidery machines. This means that a compensation would cause another mass to be connected to the other side of the oscillating mass. The disadvantage is that the rotational inertia associated with it is strongly influenced by the pivoting axis.
    The invention is therefore based on the object to perform a mass balance on oscillating driven waves of an industrial shuttle embroidery machine in an ideal manner possible.
    To solve the problem, the invention is characterized by the technical teaching of claim 1.
    3. New solution (description)
    By attaching one or more balancing masses on the rotating pivot shaft, also called needle shaft, it is possible to compensate for the imbalance of the translationally moving needles around the pivot point of this pivot shaft around the best possible.
    It uses the principle of balance of power. The laterally moved masses cause a reactive torque on the rotating shaft and in the inertial direction the forces act on tension and pressure on the bearings. To the lateral masses symmetrically arranged weights of equal mass action can cancel the forces acting radially on the shaft by equal counter forces. Thus, although the rotating total mass increases around the pivoting shaft, but this almost leads to the cancellation of the vibrations stimulating forces.
    Because such a principle of mass compensation in shuttle embroidery machines was not yet known, a one-part claim is formed after the prior art shows off-type embroidery-bound embroidery machines with rotating, but not oscillating driven pivot shafts.
    According to the invention, the compensating mass is designed so that the inertia is only slightly larger and the reaction forces that are caused by the mass that is moved, are almost compensated.
    An approximate compensation is made because the compensation of the translational movement is accomplished with a rotational movement. Therefore, a 100% compensation based on the different movements is not possible.
    The invention is based on the principle that on a rotating system at the periphery of a point is tapped, which generates a pivoting movement. The translational system consists of e.g. from the needle carrier and each attached thereto needle and the rotary system is the needle shaft.
    4. Variants
    Such, according to the invention mass balance on oscillating driven waves is preferably applied to all or for some oscillating driven waves of a shuttle embroidery machine. If the same in the following description of the mass balance is described on an oscillatingly driven needle shaft, this principle of the invention applies to all other oscillating driven waves of a shuttle embroidery machine, without the need for any special reference.
    5. Resulting advantages over the prior art
    By the invention described in 3., it is possible to shift the speed limit of the machine (maximum permissible rotation speed) upwards.
    Furthermore, components which are relieved by the force balance, less massive and thus be constructed lighter, which in turn leads to a further increase in speed or cost savings.
    A mass compensation of the connecting rod and the needle bar is preferred. The difficulty with the mass compensation of a needle system is that more or less needles are in use depending on the repeat. With a 4/4 repeat all needles are switched on, with an 8/4 repeat only half and so on. In addition to the difficulty of compensating for the translatory movement, there is the additional compensation of a variable mass.
    It is therefore arranged a balancing mass on the needle pivot shaft which acts in a certain direction.
    It rotates in one direction, so that the operation is such that the reaction forces that arise, almost compensated and it is at the same time interpreted so that the whole inertia of the system is only minimally increased.
    By using an additional mass, the reaction forces are reduced and thereby also the vibration of this system.
    Feature of the present invention is that in comparison with the prior art on the respective oscillatingly driven pivot shaft an eccentric to the center of rotation of this pivot shaft attached balance mass is present whose center of gravity approximately opposite to the connected to the oscillating driven pivot shaft output unit, e.g. is arranged in the form of a drive lever.
    With the given technical teaching, there is the advantage that a mass compensation of oscillating pivot shafts on an industrial shuttle embroidery machine is ensured, for example, in a first embodiment, the pivot shaft for the needle drive is connected to the inventive eccentric balancing mass.
    The invention also provides for the mass compensation of the pivot shaft for the drill drive, the pivot shaft for the thread guide, the pivot shaft for the presser foot and the pivot shaft for the shuttle drive. In the following description, for simplicity, the invention will be described with reference to the description of the mass compensation on the needle shaft, this is not to be understood as limiting.
    All descriptions apply equally to all other mass-compensated applications, even if this is not explicitly mentioned below.
    The connection between the pivot shaft and the balancing mass must be fixed at least in the operating state, i. the balancing mass is rotatably and immovably connected to the material of the pivot shaft.
    In a further development of the present invention, however, it is provided that the balancing mass is slidably and adjustably mounted on the outer periphery of the respective pivot shaft to perform first in the idle state a compensation settings, which is then maintained in the operating state.
    In this second embodiment, the balancing mass is temporarily displaceable and adjustable formed to the outer periphery of the respective pivot shaft and is then rotatably connected at a certain assembly time in the selected pivot position with the outer periphery of the pivot shaft.
    The invention is therefore not limited to the mass compensation of a pivot shaft for the needle drive. It is provided in further embodiments that also the pivot shaft for the drill drive and / or the pivot shaft for the thread guide and / or the pivot shaft for the shuttle drive are each formed mass-compensated within the meaning of the present invention.
    For mass compensation, i. for the attachment of an eccentric balancing mass, there are various embodiments within the scope of the invention, all of which are claimed as essential to the invention individually and / or in combination with each other.
    In a first embodiment, it is provided that the balancing mass is connected at a distance from the pivot shaft with the pivot shaft, said connection being fixed or fixed at least in the operating state. This connection between the balancing mass and the outer circumference of the pivot shaft can be done for example via a lever or via another link.
    In a second embodiment, it may be provided that the eccentrically arranged on the outer periphery of the pivot shaft balancing mass with the pivot shaft itself forms a material einein- or multi-piece part.
    In this case, there are again different embodiments. In a first embodiment, the eccentric balancing mass may be formed as an eccentric bend of a centrally mounted and oscillatingly driven pivot shaft.
    In a second embodiment, it may be provided, however, that instead of the offset individually spaced mutually spaced balancing weights are arranged eccentrically on the outer circumference of the pivot shaft to be compensated. The aforementioned bend can then be omitted and is replaced by the individual distributed over the length of the pivot shaft arranged balancing weights.
    There are various possibilities for the formation of the balancing mass. It has already been mentioned at the beginning that the compensating mass can be formed in one piece with the material of the pivot shaft and forms part of the pivot shaft.
    In another embodiment, it may be provided that the balancing material is different material from the material of the pivot shaft and, for example, from a lead or other heavier metal or plastic or other suitable material, which by a suitable (fixed or adjustable) Connection is connected to the pivot shaft. This connection can either be releasable and adjustable or it can be fixed. It is also possible to fix this balancing mass via mechanical connecting means such as clamps, couplings, screws, rivets, adhesive joints, hooks or connectors on the outer circumference of the pivot shaft.
    In a further embodiment, it may be provided that the pivot shaft is formed as a hollow shaft and in the interior of the hollow shaft, the inventive compensation mass locally and rotatably or adjustably connected to the pivot shaft itself. It is therefore an eccentric partial filling in the inner circumference of a hollow shaft designed as a pivot shaft, wherein also in this embodiment, this partial filling may be formed either in one piece with the material of the hollow shaft itself or is different material with the hollow shaft.
    In any case, it is important in this embodiment that the pivot shaft can not only be designed as a solid shaft, but also as a hollow shaft. Even with the use of a pivot shaft as a hollow shaft, it is of course possible to arrange the balancing mass on the outer circumference of this hollow shaft fixed or adjustable or just - as stated above - in the interior of the hollow shaft.
    In all embodiments in which a releasable connection between the balancing mass and the shaft is provided which is rotatably connected only during the operating state with the pivot shaft, it is possible to make this temporary connection switched on and off.
    This means that the balancing weight can be switched on and off depending on the repeat, i. E. It can be connected to the pivot shaft or be released from the pivot shaft, so that a mass balance with dissolved balancing mass in this operating condition is not or only partially.
    It has been found in the use of various reports (4/4, 8/4, 12/4 and 16/4) that a 100% compensation of different needle repeats only in certain operating conditions of the respective, to be compensated pivot shaft possible is.
    Especially with the mass compensation of the needle shaft can lead to overcompensation or undercompensation of mass balance. With a repeat of 4/4, all needles are in use on the needle side. In a repeat of 8/4 only half of the needles are in use, in a repeat of 12/4 only one third of the needles are in use and in a repeat of 16/4 only one quarter of the needles are in use.
    It follows that with a non-variable compensation and depending on the connection of the needles, i. E. Depending on the nature of the report, an undesirable overcompensation or undercompensation takes place.
    This is where the invention, which provides for switching on and off of balancing weights on the outer circumference of the respective pivot shaft to be compensated.
    This connection and disconnection can be realized in various ways.
    In a first embodiment, it may be provided that electromagnets are arranged on the outer circumference of the respective pivot shaft, which exert a force of attraction on the adhering thereto metallic balancing masses. If the power is turned off, the solenoid coil is de-energized and the balancing mass is no longer rotatably connected to the respective pivot shaft.
    There are also other Zuschaltmöglichkeiten, in particular mechanical Zuschaltmöglichkeiten or just - as shown above - via electromagnets.
    The same technique of switching on and off of balancing masses with controlled electromagnets is also possible with hollow shafts, in which the balancing mass either on the inner and / or on the outer circumference depending on the switching state of the associated electromagnet either rotatably with the compensated Swivel shaft can be coupled or not.
    Likewise, it is of course possible to add or remove corresponding balancing weights when the pivoting shaft is stationary. This can be done via all known detachable plug, clamp, adhesive or joint connections.
    In the case of the use of electromagnets, it may - be provided in accordance with the above description - to arrange the electromagnet and its power supply on the side of the pivot shaft.
    In a second embodiment, however, it may also be provided that the balancing weights are designed as electromagnets and the power is supplied either to the pivot shaft or to the balancing mass.
    If it is mentioned of a mass balance on pivot shafts, then this applies to all oscillating driven pivot shafts of an industrially operated shuttle embroidery machine. This means that the oscillatingly driven pivot shaft for the drill drive and / or the oscillatingly driven pivot shaft for the thread guide and / or the pivot shaft for the shuttle drive in the sense of the present invention can be mass-compensated.
    On the shuttle side only a single pivot shaft for the movement drive of the boat is provided in their Schiffchenlaufbahnen. In the meaning of the present invention, this oscillatingly movable pivoting shaft can also be designed to be mass-compensated with all of the previously and subsequently described exemplary embodiments.
    When it has been assumed in the above description that the mass balance takes place opposite to the power take-off point on the respective pivot shaft, this is not to be understood as limiting.
    In the context of the present invention, embodiments are described in which a mass balance takes place, which is formed eccentrically to the force application point on the pivot shaft. This applies in particular to a mass balance with a so-called compensation connecting rod. Such mass balance can be provided for all the aforementioned pivot shafts.
    In this embodiment, a balancing connecting rod is not connected in a vertical axis to the balancer shaft, but there is only an indirect connection instead by attaching a balancing connecting rod with its one end in a pivot bearing on a rotatably connected to the pivot shaft lever and the other End of the compensating connecting rod is connected via a further pivot bearing to the drive chain.
    This makes it clear that such a compensating spigot is part of the drive chain and nevertheless carries out a mass compensation of the pivoting movement of the oscillatingly driven pivot shaft, because the direction of movement of the compensating connecting rod is approximately parallel to the direction of needle movement when the pivot shaft is to be mass compensated with respect to the needle drive.
    Important in these embodiments, therefore, is the fact that a balancing mass attaches not only eccentric directly fixed to the pivot shaft, but via a lever rotatable and pivotally attaches to the pivot shaft to be compensated, but the longitudinal axis through this mass balancing connecting rod approximately parallel to the longitudinal axis of the needle drive and / or the drill drive and / or the shuttle guide track and / or the thread guide is.
    All of the aforementioned embodiments are applicable in the same way for the ship-side pivot shaft and its mass compensation, as will be described with reference to the drawings later.
    Characteristic of industrially operated shuttle embroidery machine are therefore oscillating pivot shafts, which develop large acceleration forces and consequently experience large vibrations.
    Due to the arrangement of the inventive balancing weights - as described in all embodiments above - but the inertia of the entire system is only slightly increased.
    Since angle changes take place between the oscillatingly driven pivot shaft and the linear motion drive derived therefrom, a 100% combination is not possible, but is desired.
    In the uncompensated state, there are considerable reaction forces on the oscillatingly driven pivot shafts, which according to the invention are to be compensated by the balancing weights.
    The subject of the present invention results not only from the subject matter of the individual claims, but also from the combination of the individual claims with each other.
    All information and features disclosed in the documents, including the summary, in particular the spatial design shown in the drawings, are claimed as essential to the invention, as far as they are new individually or in combination with respect to the prior art. Insofar as individual objects are designated as "essential to the invention" or "important", this does not mean that these objects necessarily have to form the subject of an independent claim. This is determined solely by the current version of the independent claim.
    In the following, the invention will be explained in more detail with reference to drawings illustrating several execution paths. Here are from the drawings and their description further features essential to the invention and advantages of the invention.
    Show it:
    [0073]<Tb> FIG. 1: <SEP> schematizes a drive arrangement for the needle drive of a shuttle embroidery machine according to the prior art<Tb> FIG. 2: <SEP> the same embodiment as in FIG. 1 with a mass-compensated pivot shaft<Tb> FIG. 3: <SEP> schematizes the operating principle of the mass-compensated pivot shaft in a first and in a second embodiment<Tb> FIG. 4: <SEP> the mass compensation of the pivot shaft in a third embodiment<Tb> FIG. 5: <SEP> A first embodiment of how the balancing mass is connected to the pivot shaft<Tb> FIG. 6: <SEP> A second embodiment of how the balancing mass can be connected to the pivot shaft<Tb> FIG. FIG. 7 shows a third embodiment, which in principle corresponds to the embodiment according to FIG. 4<Tb> FIG. 8: A fourth embodiment showing a pivot shaft designed as a hollow shaft<Tb> FIG. 9: <SEP> the compensation image of the vibration compensation in the form of compensation degree curves, which are recorded as a function of the needle repeat<Tb> FIG. 10: <SEP> a structurally executed embodiment for a mass compensation on a needle drive and a drill drive<Tb> FIG. 11: <SEP> is a larger plan view of the arrangement according to FIG. 10 in a perspective view<Tb> FIG. 12: <SEP> Another embodiment in which the balancing mass is designed as a balancing connecting rod<Tb> FIG. 13: A first embodiment with a functional representation of the functional principle according to FIG. 12<Tb> FIG. 14: <SEP> A second embodiment in comparison with FIG. 13<Tb> FIG. 15: <SEP> the drawing of the mass compensation on a ship's pivot shaft
    1, the basic drive principle for the needle side of a shuttle embroidery machine is first shown, wherein the same reference numerals have been used for the same parts according to the invention.
    All references, which are also given with reference to FIG. 1 (prior art), also apply to the same parts of the following drawings.
    A vertical shaft 1 is rotationally driven, for example, about its pivot point 2 in the direction of arrow 3 and unfolds reaction forces 4, 5 directed horizontally and vertically in this rotation.
    Eccentrically from the pivot point 2, the vertical shaft 1 is connected via a first eccentric connection 6 with a connecting rod 7, whose other end is rotatably driven by a connection 9 to a lever 10. The connecting rod 7 is thus driven in the direction of arrows 8 oscillating.
    The lever 10 is rotatably connected to the pivot shaft 11 and thus drives these oscillating in the direction of arrows 12. This produces considerable reaction forces 14, 15 in the horizontal and vertical directions.
    The pivot shaft 11 has the center of rotation 16 and at another part of the pivot shaft 11, this is non-rotatably connected via a number of drive levers 17 each with a latch lever 19.
    The connection between the drive lever 17, which is rotatably connected to the pivot shaft 11, via the connection 18 and the latch lever 19 is connected at its opposite end with a connection 20 with a needle carrier 21 which is driven to oscillate in the direction of arrows 22 is and is provided in the region of a longitudinal guide 24 at its front end with a needle 25 which is driven thereby oscillating in the direction of arrows 22.
    For the sake of simplicity, neither the fabric plane nor the stitch plate nor the ship's side arrangement is shown.
    As can be seen from the drawing according to FIG. 1 (prior art), considerable moments of inertia result from the reaction forces 4, 5 at the circumferentially driven king shaft 1 and also considerable inertia forces from the resulting reaction forces 14, 15 at the needle-side pivot shaft 11 ,
    The invention is now the mass compensation of the pivot shaft 11 (and later still to be explained further pivot shafts 31, 36, 38, 41) with an inventive balancing mass 26 which is eccentrically mounted on the outer periphery of the pivot shaft 11.
    The attachment can be temporarily releasable or permanently fixed.
    If you now a balancing mass 26, which is approximately crescent-shaped and which rests with its inner circumference on the outer circumference of the pivot shaft 11 and with respect to a vertical 27 approximately in extension to the driven-side drive lever 17, there is a desired mass compensation, as shown by the length of the now shorter illustrated arrows 14, 15.
    Although it must be accepted by the mass compensation means of the balancing mass 26, a slight increase in the reaction forces 4, 5, which now have a greater value than reaction forces 4, 5. However, this does not matter for the mass balance of a pivot shaft 11, because it matters crucially to realize the mass balance on the needle-side pivot shaft 11 to make the needle drive quieter and vibration and thus an improved needle guide, a vibration-poor needle 25 and a wear-free To allow longitudinal guide 24.
    By means of the mass compensation according to the invention with the balancing mass 26, therefore, the bearings on the connections 18, 20 are also protected, as is the longitudinal guide 24.
    It can thus at significantly higher speeds (stitch counts) a more precise longitudinal guidance of the respective needle 25 can be achieved.
    The now according to the invention minimized reaction forces 14, 15 are no longer registered in the scope - as in the prior art - in the machine structure and thus the entire machine is operated vibration and low-wear.
    This makes it possible for the first time to drive much higher speeds on such an embroidery machine.
    If in previous embroidery machines a maximum speed of about 600 revolutions / min were common, can now be driven 900 to 1200 revolutions / min, without causing deterioration of the embroidery image or premature wear of the bearings and the longitudinal guides.
    Fig. 3 shows various embodiments of the application of the balancing mass 26, wherein in Fig. 3, two different embodiments are shown.
    In a first embodiment, it may be provided that the balancing mass 26 is connected via a non-rotatably connected to the outer periphery of the pivot shaft 11 lever 28 and the balancing mass 26 is in extension of the vertical 27, which is assumed that the output side Drive lever 17 connects to this vertical 27, as shown in Fig. 3 only schematically.
    The closer the balancing mass 26 comes to the center of rotation 16 of the pivot shaft 11, as shown by the distance 57, the larger it must be, but thus the effect on the rotational inertia is smaller. The distance 57 should therefore be minimized.
    However, Fig. 3 also shows that it is possible in another embodiment, the distance 57 to extend the greatly enlarged distance 57 so that the balancing mass 26 is far away from the center of rotation 16 of the pivot shaft 11. Again, a mass compensation is possible and given. However, the balancing mass 26 results in a very high mass inertia, while the compensation mass 26, which is placed close to the center of rotation 12 at a distance 57, develops a significantly lower mass inertia.
    As a further embodiment, FIG. 4 shows that the balancing mass 26 can also be distributed directly into the mass of the pivot shaft 11, i. it forms with this either a material integral part or it is detachably or firmly connected to the outer periphery of the pivot shaft 11.
    The detachable connection is shown in Fig. 4 only with the arrow directions 29, which means that in the region of the contact surface 58, with the balancing mass 26 is connected to the outer periphery of the pivot shaft 11, a releasable connection is arranged so that the Compensation mass 26 can be moved and fixed in the circumferential direction.
    During operation, this connection should not be solvable, but with a stationary pivot shaft, the connection should be changeable. Accordingly, according to a further feature of the invention, the balancing mass 26 can be displaced along the contact surface 58 in the arrow directions 29 on the outer circumference of the pivot shaft 11 so as to allow adjustment of the compensation compensation or the elimination of machine-side tolerances.
    It has already been pointed out in the general part of the description that the contact surface 58 may be formed by any releasable and fixed connection means of mechanical, magnetic or electromagnetic type.
    In the latter case it can be provided that the balancing mass is formed as a magnetizable metal mass and in the region of the contact surface 58 are provided with power supplied electromagnets, which are supplied with power as needed and the balancing mass with the outer periphery of the pivot shaft 11 in the region of Contact area 58 couple or release. It is therefore a coupling with which the balancing mass can be coupled in a certain angular position of the pivot shaft with this rotationally fixed or can be selectively decoupled from the pivot shaft.
    Fig. 5 shows a first embodiment, where it can be seen that the pivot shaft 11 has a balancing mass in the form that the balancing mass is formed as a bend 30, which extends over the entire length of the pivot shaft 16.
    Of course, it may also be possible to use instead of a continuous bend 30 and a plurality of successive offsets 30, which also need not necessarily lie on the same plane.
    It is important that the pivot shaft in the region of the bend 30 is respectively connected to the drive levers 17 which execute the needle drive.
    Instead of a continuous or interrupted bend 30, a distribution of individual weights on the outer circumference of the pivot shaft according to FIG. 6 can also be provided.
    Here it is shown that the balancing mass 26a distributed in the form of balancing weights over the length of the pivot shaft 11 is arranged. The balance weights 26a-c need not be arranged in a single plane, they may also be mutually angularly offset on the pivot shaft 11.
    It can of course also be provided to connect the balancing weights 26a with each other, so that they give a continuous eccentrically trained, distributed over the one side of the pivot shaft arranged weight.
    Fig. 7 is approximately identical to the embodiment of FIG. 6, wherein symbolically only a single balancing mass 26 is shown instead of a plurality of balancing weights, either the balancing weights 26a are arranged separately from each other and each balancing mass associated with an associated drive lever 17 is or - not shown in the drawing - the balancing weights 26a, 26b, 26c are interconnected continuously and are arranged eccentrically on one side of the pivot shaft 11.
    The invention is not limited to all described embodiments and also in the embodiments described later, that a single balancing mass is disposed at a single point on the outer circumference of the pivot shaft. It can also be provided to arrange a plurality of balancing masses of different mass inertia at different locations of the pivot shaft and / or at different circumferential angles, in order to allow an even better mass balance.
    Thus, it can be provided that are arranged on the outer circumference of the pivot shaft at an angle to each other arranged several balancing weights, wherein a balancing mass develops a greater inertia than the other balancing weights used.
    The invention is therefore expressly not limited to the arrangement of a single balancing mass on the outer circumference of a mass-compensated pivot shaft.
    When in the above embodiments of the mass compensation of the needle drive serving pivot shaft 11 was mentioned, this is not to be understood as limiting. There are all embodiments and their explanations for the mass compensation of all oscillating driven - also described later - pivot shafts, without this requires a special further mention.
    With reference to the embodiment of FIG. 8 is also pointed out that the pivot shaft 31 can also be compensated in such a way that it is designed as a hollow shaft and in the interior 32 of such a hollow shaft, a suitable balancing mass 26 either releasably or firmly with the inner circumference of Hollow shaft is connected. Such a balancing mass can also be arranged as an eccentric, shell-shaped structure on the outer circumference of the pivot shaft 31. The internal and / or external structures of compensating masses 26 can be adjustably fixed in the circumferential direction or form a non-adjustable, non-rotatable composite with the pivot shaft 31.
    Fig. 9 shows various degrees of compensation curves 33 of the mass compensation on a pivot shaft 11, 31, wherein it can be seen that on the ordinate different degrees of compensation are recorded and a 100% compensation is possible only in certain Rapporteinstellungen while in dependence From the report also over- and undercompensations of the mass balance take place.
    The curve 33a shows a first compensation curve for a 4/4 repeat, and it can be seen that only with a 4/4 needle repeat 100% compensation takes place, while when switching to an 8/4 repeat an overcompensation of eg 150% takes place. Depending on further connectable or disconnectable needle reports, e.g. 12/4 and 16/4 overcompensate, which can go up to 200%.
    The same applies to the compensation degree curve 33b, which provides that a 100% compensation takes place in the case of a needle repeat of 8/4, while a 50% undercompensation takes place in the case of a 4/4 repeat.
    A similar subject is shown for curve 33c, which shows that only a 12/4 needle repeat has 100% compensation, while a 4/4 needle repeat has 75% undercompensation.
    By analogy, this also applies to the other compensation curves 33d and 33e.
    The group of curves 33a-33e shows that it is possible for the first time to achieve 100% compensation at position 60 in the event of overcompensation, for example at position 59, when the compensation mass increases from position 59 in the direction of position 60 is made switchable.
    Thus, even different needle repeats, which would lead to over or under compensation, be compensated by switching on and off of mass balance weights, so that always - regardless of Nadelrapport - a 100% compensation can be achieved.
    In any case, it can be seen from FIG. 9 that only in the points of intersection 34a, 34b, 34c and 34d a 100% compensation as a function of the respective needle repeat 4/4, 8/4, 12/4 and 16/4 is possible if no compensating masses which can be switched on and off are used.
    10 now shows a constructive embodiment in which a mass compensation of a pivot shaft 11 and a drill pivot shaft 36 is executed. Likewise, FIG. 10 shows how in addition, the pivot shaft 38 may be formed mass-compensated for the thread guide.
    For reasons of simplicity, Fig. 10 shows only the pivot shaft 11 for the needle drive and the associated balancing mass 26 which is located exactly diametrically opposite to the center of rotation 16 and the outgoing therefrom drive lever 17 and, for example, releasably via clamps 46 with the outer periphery of Pivot shaft 11 is connected.
    When loosening the clamps 46 thus the balancing mass 26 can be moved in the circumferential direction or in the opposite direction to the circumference on the pivot shaft 11 and then tightened again.
    In accordance with the embodiment of FIG. 2, the drive lever 17 is connected via the connection 18 with the latch lever 19, and this is connected beyond its connection 20 with a needle carrier 21. The needle carrier 21 carries on its front side the needle clamp 35. In the needle clamp 35, the embroidery needle (needle 25), not shown, is clamped.
    The same mass compensation of the oscillating driven pivot shaft 36 for the drill is realized in Fig. 10 by a further balancing mass 37 which is arranged eccentrically on the outer periphery of the pivot shaft 26 and is located opposite to the output side lever 40, at its free end is connected via a connection 43 with an oscillating driven Bohrerklinke 42, which is connected via a further connection 44 with a drill carrier 45. The recorded in the drill carrier 45 drill is not shown.
    Of course, it is also within the meaning of the present invention, only a single pivot shaft, e.g. the pivot shaft 11 and / or the pivot shaft 36 and / or the pivot shaft 38 to be provided with a mass compensation in the sense of all the above and below embodiments.
    The pivot shaft 38 for driving the thread guide is connected to the balancing mass 39. Here, the same explanations apply as were given using the balancing weights 26 and 37.
    Incidentally, the entire assembly is mounted on a machine frame 13 (cheek). The other drive members are not shown in Fig. 10.
    Fig. 11 shows a larger plan view of the arrangement of FIG. 10, where it can be seen that the balancing weights 26a-26c distributed from each other are arranged on the outer circumference of the pivot shaft 11 and releasably to slipped state in the circumferential direction and then rotatably coupled by means of the clamps 46 are arranged on the outer circumference of the pivot shaft 11.
    Thus, it is possible to set each individual balancing mass 26a independently of the other balancing mass 26b and this in turn independently of the other balancing mass 26c on the circumference of the pivot shaft 11 in the circumferential direction separately and then set using the clamp 46.
    From Fig. 11, the further details of the needle drive and the drill drive can be seen, as already indicated in Fig. 10 in an enlarged view. Overall, it can be seen that there is a high mass compensation requirement for the entire needle bed 47, because depending on the repeat only individual groups of needles are switched on or off and a mass compensation is provided by the compensation on the needle-side pivot shaft 11.
    FIG. 12 shows another compensation principle which is to enjoy protection to the same extent as the exemplary embodiments described above.
    All advantages and features of the previously described embodiments also apply to the embodiment of FIG. 12 and vice versa.
    Although the mass compensation on the needle side pivot shaft 11 will be described below. However, the same mass compensation also applies mutatis mutandis to the drill-side pivot shaft 36 and / or for filament-side pivot shaft 38 and / or for the ship-side pivot shaft 41st
    Characteristic of the embodiment of FIG. 12 is that a balancing mass 26 is not rotationally fixed (fixed or adjustable) is arranged on the outer circumference of the pivot shaft 11, but that instead the pivot shaft 11 is rotatably connected to a lever 28, at its outer free end, a first pivot bearing 48 is provided for receiving one end of a Ausgleichpleuels 61. The balancing mass 26 is thus formed by a compensation connecting rod 61.
    The other end of this compensating connecting rod 61 is connected via a further rotary bearing 49 with a reversing lever 50, which is approximately C-shaped and is pivotally received with its C-base in a machine-fixed pivot bearing 51.
    At the opposite end of the reversing lever 50, a further connection 9 is provided, which is connected to the connecting rod 7, which is connected via the connection 6 with a lever 53 which is rotatably connected to an oscillatingly driven output shaft 54. The output shaft 54 forms the output of the gearbox and is thus driven to oscillate.
    Feature of this embodiment is that no eccentric compensation takes place directly on the outer circumference of a pivot shaft 11, 31, 36, 38, 41, but according to a schematic operating principle of FIG. 13 and 14th
    It can be seen that the compensating connecting rod 61 serving for mass balance is formed with its movement axis 56 in the same direction and approximately parallel to the movement axis 55 on the needle side. That is, the needle drive with the needle carrier 21 and the needle 25 moves in a movement axis 55 which is approximately parallel to the movement axis 56 as a longitudinal axis through the compensation connecting rod 61.
    It follows that only a small distance 57 between the center of rotation 16 and the connection of the compensating connecting rod 61 is provided on the lever 28, which leads to an ideal mass compensation. The smaller this distance 57, the better the degree of compensation.
    In any case, it is important that the compensating connecting rod 61 is directed in a different direction than, for example, the compensating masses 26, 26a-26c arranged eccentrically on the outer circumference and the compensating masses 37 and 39 of the preceding drawing figures.
    It is also important that the compensating mass 26 formed by the connecting rod 61 at the same time is part of the drive chain and acts as a drive member, which leads to a simplification of the entire drive chain. It then does not have its own balancing mass 26 are arranged, as in the other embodiments as in Fig. 1 to 11, but the balancing mass 26 is integrated in the drive chain itself.
    FIG. 14 shows that, to further minimize the distance 57, it may be provided that the rotary bearing 48 is arranged in the region of the pivot shaft 11 itself.
    Thus, the distance 57 can be further minimized.
    FIG. 15 shows the mass compensation of a pivot shaft 41 on the shuttle side. Here it can be seen that it is only a single pivot shaft 41, which is mass-compensated. All previously described embodiments according to FIGS. 1 to 14 thus also apply to the mass compensation of the pivot shaft 41 on the shuttle side. In detail, the following applies:
    The balancing mass 26 is arranged on the clamp 46 in the circumferential direction adjustable and lockable on the outer circumference of the pivot shaft 41 eccentrically. Opposite to the center of gravity of the balancing mass 26, the pivot shaft 41 is connected to a lever 62, at the free end of a connection 63 is arranged for the pivotal mounting of a second lever 64, the other end of the so-called Schiffchenlineal drives (not shown) are the guide elements of this ruler attached to the flange 66.<Tb> 1 <September> Bevel<Tb> 2 <September> pivot<Tb> 3 <September> arrow<Tb> 4 <September> reaction force<Tb> 5 <September> reaction force<tb> 6 <SEP> eccentric connection<Tb> 7 <September> Rods<Tb> 8 <September> arrow directions<Tb> 9 <September> Connection<Tb> 10 <September> Lever<tb> 11 <SEP> Swing shaft (needle)<Tb> 12 <September> arrow directions<tb> 13 <SEP> Machine frame (cheek)<Tb> 14 <September> reaction force<Tb> 15 <September> reaction force<Tb> 16 <September> Turning Center<tb> 17 <SEP> Drive lever (for needle)<Tb> 18 <September> Connection<Tb> 19 <September> ratchet lever<Tb> 20 <September> Connection<Tb> 21 <September> needle carrier<Tb> 22 <September> arrow<Tb> 23 <September><Tb> 24 <September> longitudinal guide<Tb> 25 <September> Needle<tb> 26 <SEP> Leveling Compound 26a-c<tb> 26 <SEP> Compound connecting rod<tb> 26 <SEP> Compound connecting rod<Tb> 27 <September> Vertical<Tb> 28 <September> Lever<Tb> 29 <September> arrow<tb> 30 <SEP> Offset (from 11)<tb> 31 <SEP> Swivel shaft (mass compensated)<Tb> 32 <September> Interior<Tb> 33 <September> compensation degree turn<Tb> 34 <September> Intersection<Tb> 35 <September> Nadelklemmung<tb> 36 <SEP> Swivel Shaft (Drill)<tb> 37 <SEP> Leveling Compound (Drill)<tb> 38 <SEP> Swivel shaft (thread guide)<tb> 39 <SEP> Leveling Compensation (for 38)<Tb> 40 <September> Lever<tb> 41 <SEP> Swing shaft (shuttle side)<Tb> 42 <September> Drills jack<Tb> 43 <September> Connection<Tb> 44 <September> Connection<Tb> 45 <September> Drills carrier<Tb> 46 <September> Schelle<Tb> 47 <September> needle bed<Tb> 48 <September> pivot<Tb> 49 <September> pivot<Tb> 50 <September> lever<Tb> 51 <September> pivot bearings<Tb> 52 <September> pivot bearings<Tb> 53 <September> Lever<tb> 54 <SEP> Output shaft (gear box)<Tb> 55 <September> axis of movement<tb> 56 <SEP> Movement axis (balancing mass 26)<tb> 57 <SEP> distance (minimum as possible)<Tb> 58 <September> contact surface<Tb> 59 <September> Position<Tb> 60 <September> Position<Tb> 61 <September> Ausgleichspleuel<Tb> 62 <September> Lever<Tb> 63 <September> Connection<Tb> 64 <September> Lever<Tb> 65 <September> longitudinal guide<Tb> 66 <September> Schiffchenlaufbahn
    权利要求:
    Claims (10)
    [1]
    1. shuttle embroidery machine with mass balance for at least one oscillatingly driven pivot shaft (11, 31, 36, 38, 41), the pivot drive is derived from a rotationally driven, rotating kingshell (1), wherein the mass balance by at least one balancing mass (26, 26 , 26, 26a-c, 37, 39) which is connected eccentrically to the center of rotation of the pivot shaft with the pivot shaft (11, 31, 36, 38, 41).
    [2]
    2. shuttle embroidery machine according to claim 1, characterized in that the at least one balancing mass (26, 26, 26, 26a-c, 37, 39) so rotatably coupled to the pivot shaft (11, 31, 36, 38, 41) is that the center of gravity is arranged approximately opposite to the output shaft (17, 40, 62) connected to the oscillatingly driven pivot shaft.
    [3]
    3. shuttle embroidery machine according to claim 1 or 2, characterized in that the at least one compensating mass (26, 26, 26, 26a-c, 37, 39) rotationally fixed to the pivot shaft (11, 31, 36, 38, 41) connected is.
    [4]
    4. shuttle embroidery machine according to claim 1 or 2, characterized in that the at least one compensating mass (26, 26, 26, 26a-c, 37, 39) adjustable in the circumferential direction with the pivot shaft (11, 31, 36, 38, 41) is connectable.
    [5]
    5. shuttle embroidery machine according to one of claims 1 to 4, characterized in that the at least one compensating mass (26, 26, 26, 26 a-c, 37, 39) only temporarily during the pivotal movement of the pivot shaft (11, 31, 36 , 38, 41) is coupled with this.
    [6]
    6. Schiffchenstickmaschine according to one of claims 1 to 5, characterized in that the at least one balancing mass (26, 26, 26, 26a-c, 37, 39) in response to the Nadelrapport temporarily with the pivot shaft (11, 31, 36, 38, 41) is coupled.
    [7]
    7. shuttle embroidery machine according to one of claims 1 to 6, characterized in that with the at least one compensating mass (26, 26, 26, 26a-c, 37, 39) is a mass compensation of the pivot shaft (11) for the needle drive and / or the pivot shaft (36) for the drill drive and / or the pivot shaft (38) for the thread guide and / or the pivot shaft (41) for the shuttle drive and / or for the material presser drive is given.
    [8]
    8. shuttle embroidery machine with mass balance for at least one oscillatingly driven pivot shaft (11, 31, 36, 38, 41), the pivot drive is derived from a rotationally driven, rotating kingshell (1), wherein the mass balance by at least one balancing mass (26) in the formation of at least one compensating connecting rod (61) is formed, which is part of the drive chain for the pivot drive of the oscillatingly driven pivot shaft (11, 31, 36, 38, 41).
    [9]
    9. shuttle embroidery machine according to one of claims 1 to 8, characterized in that the pivot shaft (11, 31, 36, 38, 41) is designed as a hollow shaft or as a solid shaft.
    [10]
    10. shuttle embroidery machine according to claim 9, characterized in that when forming the pivot shaft (31) as a hollow shaft, the balancing weight (26, 26, 26, 26 a-c, 37, 39) either in the interior (32) of the pivot shaft (31 ) and / or on the outer circumference adjustable and / or fixed.
    类似技术:
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    DE4231834C2|2002-06-13|Tufting machine
    DE3819975C2|1995-11-09|Sewing machine
    DE102008035434B4|2015-02-05|Fabric presser of an embroidery machine
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    DE102010039198A1|2012-02-16|Vibration device for moving roller i.e. breast roller, to and fro along axis of machine e.g. fourdrinier paper machine, which is utilized for producing fibrous material web e.g. paper web, has interlockings that are provided under degrees
    DE2918460C2|1983-01-05|Cardan disk drive for a stitch forming means on a sewing machine
    AT142122B|1935-06-25|Fourdrinier section for paper, cardboard u. like machines.
    DE1597016A1|1970-08-06|Ruettel and Schuettelgeraet
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    EP1162298B1|2002-07-03|Embroidery machine
    DE4414053C2|1996-05-30|Drive system for vibratory and offset drives on warp knitting machines
    DE2407457C3|1976-11-04|
    DE2644611A1|1977-04-07|QUILTING MACHINE
    DE3321789A1|1984-12-20|SEWING MACHINE FOR PRODUCING A FASTENING SEAM AND A LOCKING SEAM
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    同族专利:
    公开号 | 公开日
    DE102015011703B4|2019-10-31|
    CH711529B1|2020-07-31|
    DE102015011703A1|2017-03-09|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE3341444C1|1983-11-17|1988-07-28|Pfaff Industriemaschinen Gmbh, 6750 Kaiserslautern|Drive for a stitch-forming agent on a sewing machine|
    US4966042A|1989-02-06|1990-10-30|Brown Arthur E|Balanced reciprocating machines|
    DE29710108U1|1996-06-13|1997-08-14|S & W Engineering Gmbh|1st order mass balance embroidery machine|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    DE102015011703.3A|DE102015011703B4|2015-09-05|2015-09-05|Shuttle embroidery machine with mass compensation of the oscillating waves|
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