WO1998008002A2 - A method of balancing the dynamic effects of a material body with a periodic reversing motion and a device for carrying out the method - Google Patents

A method of balancing the dynamic effects of a material body with a periodic reversing motion and a device for carrying out the method Download PDF

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Publication number
WO1998008002A2
WO1998008002A2 PCT/CZ1997/000026 CZ9700026W WO9808002A2 WO 1998008002 A2 WO1998008002 A2 WO 1998008002A2 CZ 9700026 W CZ9700026 W CZ 9700026W WO 9808002 A2 WO9808002 A2 WO 9808002A2
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WO
WIPO (PCT)
Prior art keywords
material body
balancing
balanced
motion
carrying
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Application number
PCT/CZ1997/000026
Other languages
French (fr)
Other versions
WO1998008002A3 (en
Inventor
Zdenek Koloc
Bohumír PLAC^¿EK
Jir^¿í MLYNÁR^¿
Petr Karel
Original Assignee
Vyzkumny Ústav Textilních Stroju
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
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Application filed by Vyzkumny Ústav Textilních Stroju filed Critical Vyzkumny Ústav Textilních Stroju
Publication of WO1998008002A2 publication Critical patent/WO1998008002A2/en
Publication of WO1998008002A3 publication Critical patent/WO1998008002A3/en

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Classifications

    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03D—WOVEN FABRICS; METHODS OF WEAVING; LOOMS
    • D03D49/00—Details or constructional features not specially adapted for looms of a particular type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
    • F16F15/06—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with metal springs
    • F16F15/063—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with metal springs with bars or tubes used as torsional elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/22—Compensation of inertia forces

Definitions

  • the invention relates to a method of balancing the dynamic effects of a material body with a periodic reversing motion by means of a balancing material body.
  • the invention also proposes a device for carrying out the method
  • the inertial effects of each body or the specific components of such effects or the resulting inertial effects of a plurality of bodies have been balanced by inertial effects of each balancing body or by inertial effects of a plurality of balancing bodies.
  • the balancing body/bodies is/are attached to a suitable section of the mechanism to be balanced or of an auxiliary mechanism by means of a mechanism comprising rigid members such as gear wheels or articulation mechanisms.
  • the motion of the balancing body is periodic and opposite in direction to the motion of the component to be balanced.
  • the aim to be achieved by such balancing consists in reducing the effects acting in the mechanism and spreading to its surroundings, i.e., in most cases, to the machine frame.
  • Relevant for the function of such balancing bodies is the motion that would be effected by an absolutely rigid mechanism. Both the compliance and the oscillations of the mechanism have no influence on the function of the balancing body Consequently, the effect of the balancing of the mechanism in this way does not depend on its operating frequency
  • Its drawback consists in high stress imposed on some parts of the mechanism, in particular of the drive mechanism balancing the periodic motions both of the component to be balanced and of the balancing body
  • Another well-known method of balancing the dynamic effects of a material body carrying out a periodic reversing motion consists in the application of a dynamic absorber This method is used in order to reduce the machine frame oscillations
  • the balancing body is attached by means of an elastic member to the section of the machine where the oscillations shall be suppressed, and represents a system of the balancing body with elastic coupling
  • said balancing body can rotate or slide only in the direction in which the oscillations shall be suppressed
  • the mass of the balancing body and the compliance of the elastic member attaching it to the frame are selected so as to ensure, at the operation speed, such oscillations of the balancing body as are required to suppress said oscillations of the frame This is achieved by the resonance tumng of the system of the balancing body with elastic coupling
  • the aim of the proposed method of balancing is the balancing or reduction of dynamic effects of a material body carrying out a pe ⁇ odic reversing motion, and the creation of a device for carrying out this method of balancing
  • the principle of the device for carrying out the method of balancing according to the invention consists in that the material balancing body is connected with the material body to be balanced by means of a coupling comprising an elastic member.
  • the balancing material body is mounted movable with respect both to the machine frame and to the material body to be balanced, due to the elastic member inserted between said bodies. Then, the balancing material body carries out a periodic reversing motion in the direction opposite to the component to be balanced of the inertial effects of the material body and thus creates balancing inertial effects reducing the inertial effects to be balanced.
  • the advantage of the proposed method of, and device for, balancing the dynamic effects of the material body with periodic reversing motion consists in the reduction of the stress the drive mechanism is exposed to in a stabilized state under the force action of the compensation system consisting of the balancing material body and the elastic member, on the material body to be balanced
  • Another advantage of the proposed solution consists in the elimination of the need to tune the compensation system exactly to the exciting frequency as is the case in dynamic absorbers requiring great intensification.
  • the amplitudes of the periodic reversing motion are comparable or inferior to the amplitudes of the harmonic components of the periodic reversing motion of the material body to be balanced.
  • a device which principle consists in that one end of the material body to be balanced has attached thereto, in the rotation axis of the body, one end of a torsion spring mounted for rotation in the machine frame and having fastened thereto the balancing material body.
  • the material balancing body is preferably mounted on the free end of the torsion spring from the outer side of the machine frame.
  • FIG. 1 An example of embodiment of the device for carrying out the method of balancing according to the invention is schematically shown in Fig. 1 relating to the balancing of the batten of a weaving machine.
  • FIG. 2 a schematic representation of the beat-up mechanism of the weaving machine
  • Fig. 3 the dependance of the rotation angle of the batten on the rotation angle of the crank of a four-linked mechanism
  • Fig. 4 the dependance of the angular acceleration of the batten on the rotation angle of the crank of the four-linked mechanism
  • Fig. 5 the dependance of the moment acting into the machine frame on the rotation angle of the crank of the four-linked mechanism.
  • a batten I is in a well-known way rotatably mounted in a frame 2 of a weaving machine and is in a well-known way coupled with a well-known four-linked mechanism 3 coupled with a wellknown not represented drive of the weaving machine
  • the batten i is the driven member of the four-linked mechanism 3 receiving from it its swinging motion, i e , its reversing rotary motion around the rotation axis U . of the batten I
  • the well-known four-linked mechanism 3 consists of the frame 2 having housed therein a crank 3 _ coupled with a well-known not represented drive and adapted to turn around the rotation axis 311 of the crank 3_1
  • a crank arm 32 Rotatably mounted on the crank 3_1 there is a crank arm 32 rotatably connected with the batten 1, the latter being at the same time mounted in the frame 2 of the weaving machine rotatably around the axis JJ . of rotation of the batten I
  • a torsion spring 4 mounted near its other end rotatably in the frame 2 of the weaving machine, for instance by means of a bearing 5, the other end of the torsion spring 4 having fixed thereto a balancing material body 6
  • the balancing material body 6 and the torsion spring 4 form together a compensation system whose natural frequency, determined by the mass of the balancing material body 6 and the elasticity of the torsion spring 4, is inferior to the frequency of the to-be-balanced harmonic component of the dynamic effects of the batten i so that the compensation system is excited in an over-resonance way, thus achieving the above effect
  • the motion of the balancing material body 6 is opposite in direction to the motion of the material body to be balanced In case of an ideally rigid coupling without the elastic member or in case of a sub-resonance excitation, the balancing material body 6 would move concurrently with the material body to be balanced
  • the dynamic effects of the moving balancing body 6 are in the described example of embodiment opposite and compensate the dynamic effects of the to-be-balanced harmonic component of the dynamic effects generated by the reversing rotary motion of the batten 1 At the same time, the energy produced by the moving balancing material body 6 and by the torsion spring 4 being twisted is accumulated and transmitted to the batten 1 thus reducing the stress imposed on the drive four-linked mechanism 3
  • Fig 2 shows schematically a four-linked mechanism 3 acting as the beat-up mechanism of a weaving machine 1 ⁇ represents the distance between the batten rotation axis 11 . and the axis 311 of the drive crank 3J_, ____, the length of the crank 31; J , the length of the crank arm 32, and j, the distance between the rotation axis 11 of the batten 1 and the axis of connection with the crank arm 32.
  • the other symbols mean, ⁇ the angular velocity of the crank 31; J ⁇ , the axial moment of inertia of the batten i, i.e , of the material body to be balanced; J, the axial moment of inertia of the balancing material body 6; ⁇ , the angle of revolution of the crank 3J . from the beat-up position; and ⁇ , the angle of rotation of the batten 1 from the beat-up position.
  • the natural frequency ⁇ of the compensation system consisting of the torsion spring 4 and the balancing material body 6 can be calculated as follows:
  • k stands for the order of the harmonic component
  • g ⁇ for the phase offset
  • m ⁇ for the moment related to the k-th harmonic component
  • a ⁇ for the mean value of the batten 1 rotation angle, representing the nullth harmonic component.
  • FIGs. 3 to 5 show the course of development of the angle ⁇ &_ of the batten rotation, of the angular acceleration of the batten 1, and of the moment acting into the frame 2 of the machine depending on the angle ⁇ of rotation of the crank 31 of the four-linked mechanism 3 of a given mechanism
  • the comparison of the moment M ⁇ of an unbalanced mechanism with the moment M of the mechanism balanced by the method according to this invention shows clearly the reduction of the moment M acting into the frame 2 with the balanced mechanism

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Textile Engineering (AREA)
  • Manipulator (AREA)
  • Looms (AREA)
  • Registering, Tensioning, Guiding Webs, And Rollers Therefor (AREA)

Abstract

A method of balancing the dynamic effects of a material body to be balanced and carrying out a periodic reversing motion, for instance of the batten (1) of a weaving machine, by means of a balancing material body (6) in which, under the action of both the periodic reversing motion of the material body to be balanced and of the elastic coupling between the material body to be balanced and the balancing material body (6), a periodic reversing motion of the balancing material body (6) of equal frequency, lower amplitude, and with a phase shift (π) is produced. Thus is achieved the reduction of both the dynamic effects of the material body to be balanced and of the required drive effects. The invention also proposes a device for carrying out the method.

Description

A method of balancing the dynamic effects of a material body with a periodic reversing motion and a device for carrying out the method
Technical field
The invention relates to a method of balancing the dynamic effects of a material body with a periodic reversing motion by means of a balancing material body.
The invention also proposes a device for carrying out the method
Background art
The operation of machines and mechanisms whose at least one component carries out a periodic reversing motion gives rise, due to such motion of said component (and of its drive mechanism), to inertial effects imposing stress on, and generating oscillations of, said machines or mechanisms.
Up to now, the inertial effects of each body or the specific components of such effects or the resulting inertial effects of a plurality of bodies have been balanced by inertial effects of each balancing body or by inertial effects of a plurality of balancing bodies. The balancing body/bodies is/are attached to a suitable section of the mechanism to be balanced or of an auxiliary mechanism by means of a mechanism comprising rigid members such as gear wheels or articulation mechanisms. The motion of the balancing body is periodic and opposite in direction to the motion of the component to be balanced.
The aim to be achieved by such balancing consists in reducing the effects acting in the mechanism and spreading to its surroundings, i.e., in most cases, to the machine frame. Relevant for the function of such balancing bodies is the motion that would be effected by an absolutely rigid mechanism. Both the compliance and the oscillations of the mechanism have no influence on the function of the balancing body Consequently, the effect of the balancing of the mechanism in this way does not depend on its operating frequency Its drawback consists in high stress imposed on some parts of the mechanism, in particular of the drive mechanism balancing the periodic motions both of the component to be balanced and of the balancing body
Another well-known method of balancing the dynamic effects of a material body carrying out a periodic reversing motion consists in the application of a dynamic absorber This method is used in order to reduce the machine frame oscillations The balancing body is attached by means of an elastic member to the section of the machine where the oscillations shall be suppressed, and represents a system of the balancing body with elastic coupling
In operating in this way, said balancing body can rotate or slide only in the direction in which the oscillations shall be suppressed The mass of the balancing body and the compliance of the elastic member attaching it to the frame are selected so as to ensure, at the operation speed, such oscillations of the balancing body as are required to suppress said oscillations of the frame This is achieved by the resonance tumng of the system of the balancing body with elastic coupling
Indispensable for the application of this balancing method are the frame oscillations and the compliance of the attaching member Its drawback consists in particular in its being operative only wi'thin a narrow range of operating frequency
Principle of the invention
The aim of the proposed method of balancing is the balancing or reduction of dynamic effects of a material body carrying out a peπodic reversing motion, and the creation of a device for carrying out this method of balancing
This is achieved by the method according to the invention whose principle consists in exciting, under the action of both the periodic reversing motion of the material body to be balanced and of the elastic coupling between the material body to be balanced and the balancing material body, a periodic reversible motion of the balancing material body of equal frequency but oscillating in opposite direction i.e. in opposite phase as compared with the body to be balanced. The coupling proper is such that without said elasticity the balancing material body would oscillate concurrently. In this way, the reduction of both the dynamic effects of the material body to be balanced and of the required drive effects is achieved.
This is due to the fact that in a stabilized state the sum of the kinetic energy of the material body to be balanced and of the potential energy of the elastic coupling between them is approximately constant so that the energy required for the drive need not be supplied by the drive mechanism alone as is the case of an unbalanced material body.
The principle of the device for carrying out the method of balancing according to the invention consists in that the material balancing body is connected with the material body to be balanced by means of a coupling comprising an elastic member.
Thus, the balancing material body is mounted movable with respect both to the machine frame and to the material body to be balanced, due to the elastic member inserted between said bodies. Then, the balancing material body carries out a periodic reversing motion in the direction opposite to the component to be balanced of the inertial effects of the material body and thus creates balancing inertial effects reducing the inertial effects to be balanced.
The advantage of the proposed method of, and device for, balancing the dynamic effects of the material body with periodic reversing motion consists in the reduction of the stress the drive mechanism is exposed to in a stabilized state under the force action of the compensation system consisting of the balancing material body and the elastic member, on the material body to be balanced
Another advantage of the proposed solution consists in the elimination of the need to tune the compensation system exactly to the exciting frequency as is the case in dynamic absorbers requiring great intensification. In the proposed solution, the amplitudes of the periodic reversing motion are comparable or inferior to the amplitudes of the harmonic components of the periodic reversing motion of the material body to be balanced.
To balance the dynamic effects of a material body to be balanced and carrying out a rotary reversible motion, there is proposed a device whose principle consists in that one end of the material body to be balanced has attached thereto, in the rotation axis of the body, one end of a torsion spring mounted for rotation in the machine frame and having fastened thereto the balancing material body.
The preceding embodiment can be advantageously applied on a weaving machine with its batten as the material body to be balanced
In this, the material balancing body is preferably mounted on the free end of the torsion spring from the outer side of the machine frame.
Description of the drawings
An example of embodiment of the device for carrying out the method of balancing according to the invention is schematically shown in Fig. 1 relating to the balancing of the batten of a weaving machine. To facilitate the understanding and the explanation of the effects of the invention, further drawings are attached showing, respectively, Fig. 2 a schematic representation of the beat-up mechanism of the weaving machine, Fig. 3 the dependance of the rotation angle of the batten on the rotation angle of the crank of a four-linked mechanism, Fig. 4 the dependance of the angular acceleration of the batten on the rotation angle of the crank of the four-linked mechanism, and Fig. 5 the dependance of the moment acting into the machine frame on the rotation angle of the crank of the four-linked mechanism. Specific description
The method of balancing the dynamic effects of a body to be balanced and carrying out a periodic reversing motion will be explained on a mechanism carrying out a rotary periodic reversing motion in a given angular range, i e., a swinging motion Such a mechanism is for instance the batten of a weaving machine
A batten I is in a well-known way rotatably mounted in a frame 2 of a weaving machine and is in a well-known way coupled with a well-known four-linked mechanism 3 coupled with a wellknown not represented drive of the weaving machine Thus, the batten i is the driven member of the four-linked mechanism 3 receiving from it its swinging motion, i e , its reversing rotary motion around the rotation axis U. of the batten I
The well-known four-linked mechanism 3 consists of the frame 2 having housed therein a crank 3 _ coupled with a well-known not represented drive and adapted to turn around the rotation axis 311 of the crank 3_1 Rotatably mounted on the crank 3_1 there is a crank arm 32 rotatably connected with the batten 1, the latter being at the same time mounted in the frame 2 of the weaving machine rotatably around the axis JJ. of rotation of the batten I
To one end of the batten I there is in its axis U. attached one end of a torsion spring 4 mounted near its other end rotatably in the frame 2 of the weaving machine, for instance by means of a bearing 5, the other end of the torsion spring 4 having fixed thereto a balancing material body 6
In a stabilized operation of the weaving machine, the fourlinked mechanism
3 generates a reversing rotary motion of the batten 1 exciting via the torsion spring
4 a reversing rotary motion of the balancing material body 6 having the same frequency as the reversible rotary motion of the batten I and, due to defined elasticity and mass characteristics of the torsion spring 4 and of the balancing material body 6, lower amplitude, and phase shift π The balancing material body 6 and the torsion spring 4 form together a compensation system whose natural frequency, determined by the mass of the balancing material body 6 and the elasticity of the torsion spring 4, is inferior to the frequency of the to-be-balanced harmonic component of the dynamic effects of the batten i so that the compensation system is excited in an over-resonance way, thus achieving the above effect
If the compensation system receives its over-resonance excitation from the motion of the material body to be balanced, i e , in our example of embodiment, of the batten I, the motion of the balancing material body 6 is opposite in direction to the motion of the material body to be balanced In case of an ideally rigid coupling without the elastic member or in case of a sub-resonance excitation, the balancing material body 6 would move concurrently with the material body to be balanced
As may be seen from the above description, the dynamic effects of the moving balancing body 6 are in the described example of embodiment opposite and compensate the dynamic effects of the to-be-balanced harmonic component of the dynamic effects generated by the reversing rotary motion of the batten 1 At the same time, the energy produced by the moving balancing material body 6 and by the torsion spring 4 being twisted is accumulated and transmitted to the batten 1 thus reducing the stress imposed on the drive four-linked mechanism 3
Fig 2 shows schematically a four-linked mechanism 3 acting as the beat-up mechanism of a weaving machine 1^ represents the distance between the batten rotation axis 11. and the axis 311 of the drive crank 3J_, ____, the length of the crank 31; J, the length of the crank arm 32, and j, the distance between the rotation axis 11 of the batten 1 and the axis of connection with the crank arm 32. The other symbols mean, ω the angular velocity of the crank 31; J^, the axial moment of inertia of the batten i, i.e , of the material body to be balanced; J, the axial moment of inertia of the balancing material body 6; τ, the angle of revolution of the crank 3J. from the beat-up position; and ϋ, the angle of rotation of the batten 1 from the beat-up position.
If, in a specific mechanism, the above values as well as the rigidity constant c of the torsion spring 4 are known, the natural frequency Ω of the compensation system consisting of the torsion spring 4 and the balancing material body 6 can be calculated as follows:
Ω 4- rad / s
The balancing of the first harmonic component is governed by the following equation:
Figure imgf000009_0001
The moment transmitted into the machine frame 2 by an unbalanced mechanism:
0 (τ) = ∑ mo k sin(kτ + φk ) , m0 k = J 0ak (kω): k.l
The moment transmitted into the machine frame 2 by a balanced mechanism:
J
M(τ) = mk sin(kτ + φk ) , mk = J„ + ak (kω)3 k-l kω ~Ω
The angle of rotation of the batten 1 during a uniform turning of the crank 3J_:
Figure imgf000009_0002
where: k stands for the order of the harmonic component; g^, for the phase offset; m^ for the moment related to the k-th harmonic component; a^, for the mean value of the batten 1 rotation angle, representing the nullth harmonic component.
To understand better the effects of the invention, Figs. 3 to 5 show the course of development of the angle ■&_ of the batten rotation, of the angular acceleration of the batten 1, and of the moment acting into the frame 2 of the machine depending on the angle τ of rotation of the crank 31 of the four-linked mechanism 3 of a given mechanism The comparison of the moment M^ of an unbalanced mechanism with the moment M of the mechanism balanced by the method according to this invention shows clearly the reduction of the moment M acting into the frame 2 with the balanced mechanism
Dynamic effects arising during reversing rectilinear motion of a material body can by balanced in a similar way

Claims

PATENT CLAIMS
1. A method of balancing the dynamic effects of a material body to be balanced and carrying out a periodic reversing motion, characterized by exciting, under the action of both the periodic reversing motion of the material body to be balanced and of the elastic coupling between the material body to be balanced and the balancing material body (6), a periodic reversing motion of the balancing material body {6) of equal frequency but with a phase shift (π), thus reducing both the dynamic effects of the material body to be balanced and the required drive effects
2. A device for carrying out the method as claimed in Claim 1, characterized by that the balancing material body (6) is connected with the material body to be balanced by means of a coupling comprising an elastic member
3. A device as claimed in Claim 2, characterized by that the material body to be balanced consists of a material body intended to carry out a rotary reversible motion and having attached to one of its ends in its rotation axis one end of a torsion spring (4) mounted for rotation in the frame (2) of a machine and having fixed thereto the balancing material body.
4. A device as claimed in Claim 3, characterized by that the material body to be balanced is the batten (1) of a weaving machine.
5. A device as claimed in Claim 3 or 4, characterized by that the balancing material body (6) is fixed to the torsion spring (4) from the outer side of the machine frame (2).
PCT/CZ1997/000026 1996-08-19 1997-07-24 A method of balancing the dynamic effects of a material body with a periodic reversing motion and a device for carrying out the method WO1998008002A2 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CZPV2440-96 1996-08-19
CZ962440A CZ284099B6 (en) 1996-08-19 1996-08-19 Process of balancing dynamic effects of a mass body producing periodic reversing motion and apparatus for making the same

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WO1998008002A3 WO1998008002A3 (en) 1998-03-26

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2372185A3 (en) * 2010-03-29 2017-10-25 VÚTS, a.s. Method and device for reducing of negative effects of dynamic forces of mechanical system
CN114990765A (en) * 2022-07-06 2022-09-02 天津工业大学 Reed motion path planning and driving control method for spacer fabric

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CZ306815B6 (en) * 2016-08-04 2017-07-19 VĂšTS, a.s. A method of damping vibrations with a drive device and a device for performing this method.

Citations (6)

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Publication number Priority date Publication date Assignee Title
FR1162857A (en) * 1956-12-19 1958-09-18 Hydraulic shock absorber for loom shuttles
US3866482A (en) * 1972-08-08 1975-02-18 Voest Ag Drive system for reed roller of weaving machine
US4069967A (en) * 1976-10-14 1978-01-24 Bird Machine Company, Inc. Centrifuge with chatter suppression
US4240471A (en) * 1977-09-07 1980-12-23 Vyzkumny A Vyvojovy Ustav Zavodu Vseobecneho Strojirenstvi Loom back rest mechanism
DE3610321A1 (en) * 1986-03-26 1987-10-01 Hasse & Wrede Gmbh Torsional vibration absorber with viscous damping medium
FR2710381A1 (en) * 1993-09-23 1995-03-31 Hutchinson Damper (oscillator) for vibrating bar

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1162857A (en) * 1956-12-19 1958-09-18 Hydraulic shock absorber for loom shuttles
US3866482A (en) * 1972-08-08 1975-02-18 Voest Ag Drive system for reed roller of weaving machine
US4069967A (en) * 1976-10-14 1978-01-24 Bird Machine Company, Inc. Centrifuge with chatter suppression
US4240471A (en) * 1977-09-07 1980-12-23 Vyzkumny A Vyvojovy Ustav Zavodu Vseobecneho Strojirenstvi Loom back rest mechanism
DE3610321A1 (en) * 1986-03-26 1987-10-01 Hasse & Wrede Gmbh Torsional vibration absorber with viscous damping medium
FR2710381A1 (en) * 1993-09-23 1995-03-31 Hutchinson Damper (oscillator) for vibrating bar

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2372185A3 (en) * 2010-03-29 2017-10-25 VÚTS, a.s. Method and device for reducing of negative effects of dynamic forces of mechanical system
CN114990765A (en) * 2022-07-06 2022-09-02 天津工业大学 Reed motion path planning and driving control method for spacer fabric

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CZ284099B6 (en) 1998-08-12
WO1998008002A3 (en) 1998-03-26

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