• 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:
    It embroidery machine comprises a vibration compensator (2) having at least one mass body (21a, 21b, 21c, 21d) which is connected to the machine frame and which is adapted to exert compensation forces on the machine frame, which from the stitch forming organs on the machine frame in the direction of action counteract the sticking needles (11) applied forces. As a result, vibrations or vibrations of the machine frame are minimized.
    公开号:CH710639A1
    申请号:CH00070/15
    申请日:2015-01-20
    公开日:2016-07-29
    发明作者:Lässer Franz
    申请人:Lässer Ag；
    IPC主号:
    专利说明:

    The invention relates to an embroidery machine, a vibration compensator for an embroidery machine and a method for compensating vibrations in an embroidery machine according to the preambles of claims 1, 8 and 9.
    In embroidery machines, especially in large embroidery machines and small stitching machines and quilting machines, a plurality of stitch formation units is driven by at least one drive to execute synchronously consecutive stitch cycles. As a rule, the drive is effected by means of at least one common drive shaft, which extends over the entire length of the embroidery machine. This drive shaft is driven by at least one motor and drives stitch forming members or embroidery tools of a plurality of stitch forming units. In particular, the needle tappets, the thread guides and the presser foot are cyclically moved transversely to the drive shaft for each coupled embroidery point according to predetermined movement patterns. Such an embroidery machine is known for example from CH 691 688 A5.
    In general, the stitch formation organs are mounted on the machine frame. They are in particular arranged on a support or needle carriage, which is formed on the machine frame or connected to the machine frame. In small knitting machines, a plurality of needle heads, each of which comprises a plurality of needle plungers, are mounted so as to be displaceable together on the carrier in the longitudinal direction of the drive shaft. Only those needle tappets are coupled to the drive whose position coincides with the coupling positions on the carrier.
    For large embroidery machines, however, the positions of the individual embroidery sites are fixed. At each point of embroidery, an element for individual decoupling of the associated Nadelpleuels is provided by the on-off shaft.
    When embroidering forces or periodic force curves are exerted on the carrier or the machine frame on the bearings of the stitch formation organs. These forces are caused by the acceleration of masses of the stitch formation organs. The forces acting on the machine frame mass forces are dependent on the number and location of the coupled with the drive embroidery sites. The embroidery sites are distributed over the length of the drive shaft. For small knitting machines, this length is typically on the order of ten meters. For large embroidery machines, it can be up to thirty meters. The mass forces of the stitch formation organs can vary depending on the respective configuration of active and inactive embroidery sites. The temporal course of the mass forces results from a superimposition of the different movements of different stitch formation members, which are mounted at different locations of the machine frame.
    Of secondary importance are other forces acting on the carrier, e.g. the force when pressing the presser finger on the fabric to be embroidered. Such forces acting periodically on the machine frame can cause unwanted vibrations or vibrations of the carrier or the machine frame. Depending on the speed of the drive shaft, the superposition of vibrations may have resonances with relatively high oscillation amplitudes. Such positive superpositions of vibrations are not only perceptible as disturbing noise. They can also have a restrictive effect on the usable speed range of the machine, since vibrations of the machine frame are also transmitted to the stitch formation members. A smaller maximum speed means a low maximum performance and thus a lower productivity of the embroidery machine. Conventional approaches to reduce disturbing vibrations or vibrations of the machine frame are e.g. local adjustments to the machine frame and / or the foundation on which the machine frame is anchored. In particular, e.g. locally increases the rigidity or strength of the machine frame and / or increased at certain points of the machine frame and / or the foundation of the mass. In addition, a larger proportion of material expensive such machines, but essentially causes only a shift in the limit speed towards higher frequencies.
    An object of the present invention is to provide an embroidery machine, are effectively reduced in the vibration caused by stitch forming organs vibrations or vibrations of the machine frame.
    This object is achieved by an embroidery machine, by a vibration compensator for an embroidery machine and by a method for reducing vibrations in an embroidery machine according to the features of patent claims 1 and 8 and 9.
    The embroidery machine comprises at least one connected to the machine frame vibration compensator with at least one mass body which is drivable synchronously to the drive shaft for performing a cyclic movement sequence. By accelerations of this mass body or these mass body forces or periodic force curves are exerted on the machine frame, which counteract the force curves of the stitch formation members such that the resulting oscillation amplitude of the machine frame is reduced or minimized. The force effects on the machine frame caused by the stitch formation organs are thus at least partially compensated by the force curves caused by the vibration compensator. Complete extinction or compensation of the vibrations or the forces causing them is not possible because of the complexity of the system, in particular because of the different coupling points of the forces acting on the machine frame.
    Without further reference, the expression "compensation" is to be understood as "partial compensation", the oscillation compensator exerting a force curve as complementary as possible to the force curve of the stitch-forming organs on the machine frame and thus reducing or minimizing the oscillation amplitude of the machine frame.
    Preferably, the drive of the mass body by mechanical coupling with the drive shaft of the embroidery machine. In particular, the mass body or one of the mass body can be connected eccentrically directly to the drive shaft.
    Additionally or alternatively to the drive shaft other or further balance shafts may be provided, which are aligned parallel to the drive shaft and with the same or opposite direction of rotation with the predetermined by the drive shaft base speed or a multiple of this basic speed can be driven.
    Preferably, each vibration compensator for the base speed and at least one additional speed each comprises two balance shafts with opposite directions of rotation. The mass body of two balancing shafts with the same speed are the same design and attached to these balancer shafts that their centrifugal forces positively overlap or add in the direction of the needle sticks, on the other hand cancel in transverse direction.
    The angular positions of the mass body to the synchronous to the drive shaft rotatable balancing shafts are adjusted so that the force caused by the vibration compensator during rotation of the drive shaft during one revolution of the main shaft is optimally complementary to the force curve of the stitch-forming organs.
    To prove particularly advantageous for the transmission of motion between rotatable shafts timing belt, since they are maintenance-free and operate quietly compared to gears. This applies both to the motion transmission from the drive shaft of the embroidery machine to a parallel main shaft or first balance shaft of the vibration compensator and for the transmission of movements to possibly existing further rotatable balance shafts of the vibration compensator. The ratio between the speed of the first balance shaft and the drive shaft is fixed by the operative connection by means of toothed belt. Preferably, this first ratio is 1: 1, as a rule, a complete stitch cycle is performed per revolution of the drive shaft. Due to the reciprocating motion of the stitch formation members during a stitch cycle, this also corresponds to the fundamental frequency of the forces transmitted to the machine frame.
    The transfer of forces in the big embroidery machine to the machine frame is mainly caused by the horizontal reciprocating motion of the stitch forming members transversely to the drive shaft in the effective direction of the needles, as these torques exert on the machine frame, which anchors down to a foundation with large mass is. Forces which act on the machine frame in the vertical direction or in the direction of the foundation when driving the stitch formation members are of secondary importance for the vibration compensator. Therefore, in a first approximation, it is sufficient to design the vibration compensator so that it can reduce vibration amplitudes of the machine frame in the horizontal direction.
    In a preferred embodiment of the invention, the delimitation of the compensation direction of centrifugal forces is achieved in that the vibration compensator in addition to the first balance shaft comprises a parallel second balance shaft which is coupled to the first balance shaft, that they can be driven with opposite rotation and the same speed is. At the two balance shafts eccentric mass body are arranged and designed so that their forces exerted on the respective shafts centrifugal forces in the direction of the reciprocating motion of the stitch forming members add and transverse to it, so at least approximately completely compensate in the vertical direction. The angles of the eccentric mass body on the balance shafts are set so that their centrifugal forces are directed against those of the stitch forming members in the direction of the reciprocation of these organs. With a suitable mass and arrangement of the eccentric mass body, the amplitude of the vibrations caused by the stitch formation organs of the machine frame can already be significantly reduced.
    Since the time sequences of the cyclic movements of the stitch formation organs with respect to a sinusoidal movement deviations and thus also additionally have different accelerations and decelerations, and the transmitted to the machine frame vibrations have no pure sinusoidal shape. In addition, vibrations of stitch formation organs of a multiplicity of embroidery locations, which are arranged along the drive shaft, overlap on the machine frame. The time course of the oscillation or the deflection with respect to the rest position at a certain point of the machine frame and in particular their maximum values are dependent on various factors. Such factors are, for example, the number and arrangement of support points at which the machine frame is anchored to the foundation, the position on the machine frame, in particular the distances to adjacent support points of the machine frame and the number and arrangement of active needle plunger.
    Despite this complexity, the invention shows a way on how the vibrations transmitted to the machine frame can be further reduced. A further analysis of the sequence of movements or the accelerations of the masses of the stitch formation members shows that one or more of the following measures can be used to achieve a further optimization of the reduction of vibrations of the machine frame.
    The formation of the vibration compensator for generating vibrations of at least one higher order, so for example vibrations with two, three or four times the frequency specified by the speed of the drive shaft fundamental frequency. This can be done analogously to the generation of the vibrations with the fundamental frequency, wherein two further balance shafts are driven by eccentric mass bodies and opposite direction of rotation via a gear with the corresponding ratio of the drive shaft. Again, the masses of the mass body whose radial distance from the respective axes of rotation and their angular position are set so that the maxima caused by the stitch formation organs resulting vibration of the machine frame is further minimized even with these balancing shafts higher order.
    Instead of a single vibration compensator, a plurality of vibration compensators, e.g. evenly distributed and fixed. The position of the vibration compensator (s) relative to the adjacent support points of the machine frame can influence the initiation and effect of the compensation forces generated by the vibration compensators. In small knitting machines to be embroidered fabric under the needle carriage or carrier is kept taut in a horizontal plane. The needle carriage is therefore anchored only at its two ends, whereby the unsupported area between these support points is comparatively long.
    For large embroidery machines, however, the needle carriage is supported at a plurality of support points, which are generally distributed at intervals of the order of about two meters over the entire length of the machine frame. In such embroidery machines, the vibration compensators are preferably arranged at the support points.
    The suitable for the individual vibration compensators balancing weights and the distances of the centers of gravity of these balancing weights of the axes of rotation of the associated balance shafts are determined so that the resulting force component of these balancing masses in the effective direction of the needles when turning the drive shaft of the corresponding resultant force component of the stitch-forming organs as well as possible counteracts. If a plurality of vibration compensators are attached to the machine frame, the machine frame is divided longitudinally into a plurality of corresponding effective portions. In order to determine the appropriate balancing weights, only the force components of the stitch-forming organs in each case the same effective section are considered in each of the vibration compensators.
    The resulting force component of the stitch-forming organs in an active section is a periodic function that can be represented as a Fourier series. The first Fourier coefficient corresponds to the component of force compensated in this effective section by the centrifugal forces of the two eccentric masses held at the balance shafts rotating at the fundamental frequency.
    The second Fourier coefficient corresponds in an analogous manner to that force component which is compensated in this effective section by the centrifugal forces of the two eccentric mass bodies, which are held at the balancing shafts rotating at twice the fundamental frequency. From the centrifugal force can be determined for each of the mass body at a given distance of the center of gravity of the axis of rotation of the associated drive shaft, the required mass or vice versa.
    Alternatively, the determination of suitable balancing weights and suitable distances of the centers of gravity of these balancing weights of the respective axes of rotation can also be done experimentally. In this case, for different constellations of the mass body, the vibration behavior of the machine either subjectively by the perception of a person or objectively by means of suitable vibration sensors, which detect the vibrations of the machine frame, preferably direction-dependent, are assessed.
    In an alternative embodiment of the invention, the balance shafts of the Schwingungskompensators could also be driven by a separate drive, for example by a servo motor, wherein the rotational speed and phase angle are controlled or regulated by sensory detected vibrations of the machine frame.
    Based on some figures, the invention will be described in more detail below. Show<Tb> FIG. 1 <SEP> a cross-section of an embroidery machine in the region of the stitch forming members, as known from the prior art,<Tb> FIG. 2 <SEP> is a diagram with cyclic movements of stitch forming members in an embroidery machine,<Tb> FIG. 3 <SEP> a diagram with position, speed and acceleration characteristics of an embroidery needle during the execution of a stitch cycle,<Tb> FIG. 4 <SEP> a force-time diagram with the force curves of two compensation masses and the force curve of the resulting compensation force,<Tb> FIG. 5 <SEP> a force-time diagram with the resulting force curves applied to the machine frame during one stitch cycle with and without compensating forces,<Tb> FIG. 6 <SEP> a partial perspective view of an embroidery machine with a vibration compensator,<Tb> FIG. 7 <SEP> a cross section of the arrangement of Fig. 5,<Tb> FIG. 8 <SEP> is a plan view of the arrangement of FIG. 5.
    Fig. 1 shows a cross section of a conventional embroidery machine in the area of an embroidery point. On a machine frame 1, a plurality of drive shafts 3 are mounted parallel to each other, which drive by means of cams 5 and roller levers 7 Stichbildungsorgane for carrying out cyclic movement sequences. In particular, in a plurality in the longitudinal direction of the drive shafts 3 side by side arranged embroidery pins tappets 9 are attached to which embroidery needles 11, thread guide 13 and presser 15 synchronously to the rotational speed of the drive shafts 3 in the effective direction of the embroidery needles 11 moves back and forth, which by the double arrows PI, P2 and P3 in Fig. 1 is shown. The needle plungers 9 are coupled via Nadelpleuel 10 with an on-off shaft 12 which are pivotable by the roller lever 7 by means of cranks 8 about a pivot shaft 14 (Fig. 6).
    The stitch forming members are mounted on a support 17 of the machine frame 1. When embroidering forces or torques are exerted on the machine frame 1 in particular by accelerated masses of stitch forming organs. The resulting force curves are repeated at each stitch cycle and can cause vibrations or vibrations of the machine frame 1.
    Fig. 2 shows for a standard embroidery machine, as it is known from "Embroidery techniques", textbook of hand and machine embroidery by Friedrich Schoner and Klaus Freier, pp. 60-63, VEB Fachbuchverlag Leipzig 1982, in a Weg- Time diagram the timing of the movements of the needle tappet 9 (curve K1), the thread guide 13 (curve K2) and the fabric presser 15 (curve K3) in the effective direction of the embroidery needle 11 during a stitch cycle, resulting in a full rotation of the drive shafts 3 by 360 ° equivalent. The direction of the abscissa corresponds to the time t, the direction of the ordinate of the position s. Fig. 3 shows in a diagram for the movement of the needle tappet 9 and the stroke of the needle 11 during a stitch cycle in addition to the curve K1 whose first time derivative or the speed (curve K1) and the second time derivative or acceleration (Curve K1). The time t is entered in the direction of the abscissa. In the direction of the ordinate, the position s is shown for the curve K1, the speed v for the curve K1 and the acceleration a of the needle tappets 9 for the curve K1. The acceleration curve K1, in conjunction with the mass of the stitch formation member, also represents the forces exerted by this stitch formation member on the machine frame 1 during one stitch cycle or the corresponding force profile in the effective direction of the embroidery needles 11. The force profile results from multiplication of the acceleration values with the accelerated embroidery stitch masses , This force profile for moving the embroidery needles 11 has two maxima and two minima during one stitch cycle.
    In an analogous manner, the forces exerted by the other stitch forming members on the machine frame 1 forces are calculated and then added to a resulting force curve.
    Fig. 4 shows in a force-time diagram, the force curves of two eccentric mass body 21 of balance shafts 23, which rotate with two times (dotted curve A) and three times (broken curve B) basic speed. The solid curve C shows the resulting superposition of the force curves A and B compensation force curve. FIG. 5 shows, in a force-time diagram through the interrupted line R1, the resultant force F or the resulting force curve which the stitch formation members jointly exert on the machine frame 1. In addition, as a solid line R2, the resulting total force curve is shown, which results from superposition with the forces exerted by the vibration compensator 2 on the machine frame 1 forces. The resulting force curve R1 of the stitch formation members is a periodic function and can therefore be represented as Fourier series or decomposed into a superimposition of sinusoidal oscillations whose frequencies are the fundamental frequency or the rotational speed of the drive shaft 3 and integer multiples thereof. In general, a force curve in a first approximation can be represented solely by an oscillation with the fundamental frequency or an integral multiple of the fundamental frequency. By considering additional additional frequency components of the force curve can be displayed in more detail. The weighting of the individual frequency components corresponds to the centrifugal forces generated by the corresponding eccentric mass bodies 21.
    According to the invention, at least one vibration compensator 2 is now attached to the machine frame 1, which is designed to exert compensation forces on the machine frame 1, which counteract the forces of the stitch formation members and at least partially cancel them. As a result, vibrations or general vibrations of the machine frame 1 can be prevented or at least significantly reduced. Each vibration compensator 2 comprises at least one mass body 21, which is drivable in synchronism with the movement of the drive shaft 3 for performing cyclic motion sequences, which caused by accelerations of this at least one mass body 21 compensation forces are transmitted to the machine frame 1, the forces of the stitch formation organs at least in or opposite counteract the effective direction of the embroidery needles 11 and compensate for this at least partially. As a result, vibrations or general vibrations of the machine frame 1 during embroidering can be significantly reduced. This in turn allows embroidering at much higher speeds.
    Fig. 6 shows a partial perspective view of an embroidery machine with a preferred embodiment of the vibration compensator 1. Fig. 7 shows a cross section of the arrangement of Fig. 6 and Fig. 8 is a plan view. The vibration compensator comprises a total of four mass bodies 21a, 21b, 21c, 21d, e.g. by means of pipe clamps on parallel to the main or drive shaft 3 aligned, rotatably mounted balance shafts 23a, 23b, 23c, 23d are fixed so that their center of mass is eccentric or at a predetermined radial distance from the respective axis of rotation. Since the first mass body 21a is fixed to the drive shaft 3, this also has the function of the first balance shaft 23a. The further balance shafts 23b, 23c, 23d are rotatably mounted in a housing (not shown), said housing being rigidly connected to the machine frame 1 (not shown) for transmitting forces, in particular being screwed tight to the machine frame 1. With such Schwingungskompensatoren 1 also existing embroidery machines can be retrofitted easily. Alternatively, the first balance shaft 23a could be arranged independently of the drive shaft 3 within the housing. By attaching the first mass body 21a to the drive shaft 3, however, space can be saved. The housing of such vibration compensators 1 can be constructed comparatively compact.
    Preferably, the vibration compensators 1 and differential gear are arranged within the embroidery machine, where they do not hinder the course of the thread and where there is no risk of injury. Of course, the housing may be formed to have a protective function.
    The drive of the balance shafts 23a, 23b, 23c, 23d is effected by the drive shaft 3, wherein a first toothed belt 25 or counter belt around a driven gear 27 on the drive shaft 3 and a drive wheel 29 at an end of the balance shaft projecting from the housing 23c is looped. Due to the smaller diameter of the drive wheel 29 compared to the output gear 27, a gear ratio of e.g. 2: 1 specified. The balance shaft 23c thus rotates at twice the speed of the drive shaft 3 and with the same sense of rotation. In the interior of the housing, a double-sided toothed turning belt 30 is wrapped around a turning wheel 31c and around pulleys 31b, 31d on the balance shafts 23b, 23c, 23d in such a way that the shafts 23b, 23d can be driven in the opposite direction of rotation to the balance shaft 23c. The diameters of the turning wheel 31c and the pulleys 31b, 31d are so dimensioned that the two balance shafts 23c and 23d are driven in opposite directions at twice the speed of the drive shaft 3 and the balance shaft 23b at the same speed as the drive shaft 3, but in opposite directions is driven. The angular positions of the mass bodies 21a, 21b, 21c, 21d on the respective balance shafts 23a, 23b, 23c, 23d are set relative to each other such that the centrifugal forces of the rotating mass bodies 21a and 21b and those of the rotating mass bodies 21c and 21d in the effective direction of the embroidery needles Superimpose 11 positively and cancel orthogonal to it. Furthermore, the rotational position of the drive shaft 3 and thus also the rotational positions of the balance shafts 23a, 23b, 23c, 23d, in which the mass body 21a, 21b, 21c, 21d are aligned in the effective direction of the embroidery needles 11, set so that an optimal reduction the resulting total force curve is achieved, in which the vibrations or vibrations of the machine frame 1 are minimal. The determination of such rotational positions can e.g. mathematically, whereby that rotational position is determined at which the amplitude or the difference between the highest peak value S and the lowest peak value S of the resulting total force curve R2 is minimal. Alternatively, a suitable value for the rotational position of the drive shaft, in which the mass bodies 21a, 21b, 21c, 21d are aligned identically, can also be determined experimentally by analyzing the vibration and vibration behavior of the machine frame 1 starting from a plausible rotational position of the rotary shaft. A plausible rotational position is e.g. those in which the resulting force curve R1 of the stitch formation members has a minimum.
    By varying the masses and / or the radial position of the centers of gravity of the mass bodies 21a, 21b, 21c, 21d, the centrifugal forces of these mass bodies can be optimized as further parameters in order to minimize the overall force curve. Since vibration compensators 2 should minimize vibrations or vibrations of the machine frame 1 in different configurations of the embroidery machine with embroidery needles 11 or in different configurations, it is expedient to optimize the centrifugal forces for an embroidery machine with a reduced assembly or with a minimum assembly, if, for example, only every fourth or every eighth needle 11 is equipped.
    In alternative embodiments, the vibration compensator 2 may be e.g. comprise only one mass body 21a on the drive shaft 3 or only mass body 21a, 21b, which are drivable at the fundamental frequency or a multiple of the fundamental frequency or in addition further mass body 21 which are driven with one or more additional rotational speeds of higher order (not shown).
    In further alternative embodiments, the vibration compensator 2 may be e.g. an autonomous drive, in particular a servomotor for accelerating a mass body 21 for the generation of compensation forces comprise (not shown). In this case, vibrations or vibrations of the machine frame 1 are preferably detected depending on the direction by means of suitable sensors. The servo motor is controlled or regulated as a function of the detected measured variables in such a way that oscillations or vibrations are minimal (not shown). Alternatively, mass bodies 21 can also be moved linearly and accelerated in the effective direction of the embroidery needles 11. Furthermore, embroidery machines can comprise one or more vibration compensators 2 distributed in the longitudinal direction of the machine frame 1.
    Legend of the reference numbers
    [0041]<Tb> 1 <September> machine frame<Tb> 2 <September> Schwingungskompensator<Tb> 3 <September> Drive Shaft<Tb> 5 <September> cam<Tb> 7 <September> roller lever<Tb> 8 <September> Crank<Tb> 9 <September> needle plunger<Tb> 10 <September> Nadelpleuel<Tb> 11 <September> embroidery needle<Tb> 12 <September> on-off shaft<Tb> 13 <September> thread guide<Tb> 14 <September> pivot shaft<Tb> 15 <September> presser<Tb> 17 <September> carrier<tb> 21, 21a, b, c, d <SEP> mass body<tb> 23a, b, c, d <SEP> balance shaft<tb> 25 <SEP> First Timing Belt<Tb> 27 <September> output gear<Tb> 29 <September> Sprockets<Tb> 30 <September> Reversible belt<Tb> 31c <September> turning wheel<tb> 31b, d <SEP> Pulley
    权利要求:
    Claims (9)
    [1]
    1. embroidery machine, comprising at least one drive shaft (3) for driving Stichbildungsorganen at a plurality in the axial direction of the drive shaft (3) juxtaposed embroidery sites, wherein the Stichbildungsorgane on a machine frame (1) are movably mounted, and wherein the embroidery by cyclic movements of the Forces formed on the machine frame (1), characterized in that at least one vibration compensator (2) is connected to the machine frame (1), that this vibration compensator (2) comprises at least one mass body (21a, 21b, 21c, 21d) which is drivable in synchronism with the movement of the drive shaft (3) for carrying out cyclical movements, wherein compensation forces caused by accelerations of this at least one mass body (21a, 21b, 21c, 21d) are transferable to the machine frame (1) and thereby vibration or vibrations of the machine frame ( 1) can be minimized.
    [2]
    2. Embroidery machine according to claim 1, characterized in that the at least one mass body (21a, 21b, 21c, 21d) of the vibration compensator (2) on a balance shaft (23a, 23b, 23c, 23d) is fixed so that its center of gravity radially spaced to the axis of rotation of this balance shaft (23a, 23b, 23c, 23d), wherein the balance shaft (23a, 23b, 23c, 23d) is the drive shaft (3) or is arranged parallel to the drive shaft (3), and that the balance shaft (23a, 23b, 23c, 23d) can be driven by the drive shaft (3) at the rotational speed of the drive shaft (3) or an integral multiple thereof with the same or opposite rotational sense.
    [3]
    3. embroidery machine according to claim 2, characterized in that at least one balance shaft (23a, 23b, 23c, 23d) of the vibration compensator (2) is mounted in a housing, and that this housing is rigidly connected to the machine frame (1).
    [4]
    4. embroidery machine according to claim 3, characterized in that the at least one balance shaft (23a, 23b, 23c, 23d) by means of a toothed belt (25) by the drive shaft (3) is drivable.
    [5]
    5. embroidery machine according to one of claims 2 to 4, characterized in that the Schwingungskompensator (2) comprises an even number balance shafts (23a, 23b, 23c, 23d) in pairs with opposite sense of rotation and the same speed synchronously with the movement of the drive shaft (3 ), wherein the rotational speeds correspond to those of the drive shaft (3) or an integer multiple thereof.
    [6]
    6. An embroidery machine according to claim 5, characterized in that the vibration compensator (2) comprises four balance shafts (23a, 23b, 23c, 23d) and a transmission, with the two of these balance shafts (23a, 23b) in opposite directions to each other with the base speed of the drive shaft ( 3) are drivable, and with which the other two balance shafts (23c, 23d) in opposite directions to each other with twice the basic speed of the drive shaft (3) are drivable.
    [7]
    7. An embroidery machine according to claim 6, characterized in that the mass body (21a, 21b, 21c, 21d) are formed and fixed to the balance shafts (23a, 23b, 23c, 23d), that their centrifugal forces in the effective direction of the embroidery needles (11 ) positively superimpose and orthogonal to cancel.
    [8]
    8. vibration compensator (2) for an embroidery machine according to one of claims 1 to 7, characterized in that in a machine frame with the (1) connectable housing a plurality of balance shafts (23a, 23b, 23c, 23d) are mounted aligned parallel to each other that this Balancing shafts (23a, 23b, 23c, 23d) coupled to each other via a gear and a common drive wheel (29) are driven, and that the transmission is formed so that each of the balance shafts (23a, 23b, 23c, 23d) with an integer Oversize or reduction ratio is drivable.
    [9]
    9. A method for compensating vibrations in an embroidery machine, characterized in that the force exerted by the Stichorganen during a stitch cycle on the machine frame (1) force curve is determined, and in that one or more vibration compensators (2) on the machine frame (1) are attached, which generate in synchronism with the speed of the drive shaft (3) compensation forces, which counteract the forces of the Stichorgane and so minimize vibrations or vibrations of the machine frame (1).
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    同族专利:
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    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
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    法律状态:
    2018-03-15| PCOW| Change of address of patent owner(s)|Free format text: NEW ADDRESS: INDUSTRIESTRASSE 1, 9444 DIEPOLDSAU (DE) |
    优先权:
    申请号 | 申请日 | 专利标题
    CH00070/15A|CH710639B1|2015-01-20|2015-01-20|Embroidery machine, vibration compensator and method for compensating vibrations in an embroidery machine.|CH00070/15A| CH710639B1|2015-01-20|2015-01-20|Embroidery machine, vibration compensator and method for compensating vibrations in an embroidery machine.|
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