CA2287851A1 - Unbalanced vibrator for stone forming machines - Google Patents
Unbalanced vibrator for stone forming machines Download PDFInfo
- Publication number
- CA2287851A1 CA2287851A1 CA 2287851 CA2287851A CA2287851A1 CA 2287851 A1 CA2287851 A1 CA 2287851A1 CA 2287851 CA2287851 CA 2287851 CA 2287851 A CA2287851 A CA 2287851A CA 2287851 A1 CA2287851 A1 CA 2287851A1
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- Canada
- Prior art keywords
- motors
- shafts
- unbalance
- vibrating table
- unbalance shafts
- Prior art date
- Legal status (The legal status 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 status listed.)
- Abandoned
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Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B28—WORKING CEMENT, CLAY, OR STONE
- B28B—SHAPING CLAY OR OTHER CERAMIC COMPOSITIONS; SHAPING SLAG; SHAPING MIXTURES CONTAINING CEMENTITIOUS MATERIAL, e.g. PLASTER
- B28B1/00—Producing shaped prefabricated articles from the material
- B28B1/08—Producing shaped prefabricated articles from the material by vibrating or jolting
- B28B1/087—Producing shaped prefabricated articles from the material by vibrating or jolting by means acting on the mould ; Fixation thereof to the mould
- B28B1/0873—Producing shaped prefabricated articles from the material by vibrating or jolting by means acting on the mould ; Fixation thereof to the mould the mould being placed on vibrating or jolting supports, e.g. moulding tables
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
- B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
- B06B1/00—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
- B06B1/10—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy
- B06B1/16—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy operating with systems involving rotary unbalanced masses
- B06B1/161—Adjustable systems, i.e. where amplitude or direction of frequency of vibration can be varied
- B06B1/166—Where the phase-angle of masses mounted on counter-rotating shafts can be varied, e.g. variation of the vibration phase
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Manufacturing & Machinery (AREA)
- Chemical & Material Sciences (AREA)
- Ceramic Engineering (AREA)
- Apparatuses For Generation Of Mechanical Vibrations (AREA)
- Road Paving Machines (AREA)
- Control Of Multiple Motors (AREA)
Abstract
An unbalanced vibrator for compacting concrete components, in particular paving stones, during their manufacture, has a vibrating table, unbalance shafts arranged on the vibrating table, motors allocated to the unbalance shafts for driving the unbalance shafts, and a device for the control and/or regulation of the rotational speed or the relative phase position of the unbalance shafts. In order to male such a vibrating table very compact, quickly adjustable, and with uniformly rotating unbalance shafts, it is proposed to design the unbalance shafts as rotor shafts of the motors and to mount the motors on the vibrating table.
Description
TITLE OF THE nVVEN'TION
Unbalanced Vibrator For Stone Forming Macbanes BACKGROUND OF THE INVENTION
Tlxe invention relates to as unbalanced vibrator for compa,cti.ag cozrcxete components, in particular paving stones during their manufacture, the vibrator bring built into a stone forming machine. An unbalanced vibrator of this type usually has a vibrating table, on which unbalance shafts are arranged, which are driven by at least one motor, wherein a device is provided for control and/or regulation of the rotational speed or relative phase. position of the unbalance shags. A device of this type is lrnown, for example, fmm German Utility Model DE-U-29712 242_ In unbalance vibrators of this type the vibrating direction and amplitude are set via the phase position of several unbalanced masses relative to each other, wherein a correspoodi~otg regulation can lead to the forces generated by the unbalanced masses on the vibrating table becoming offset, and consequently the vibzatyx~,g table remains at rest.
However, even a slight offset angle among the unbalance shafts in their "neutral positiozr'' Ieads to a relatively stmng undesired residual vibration or oscillation of the vibrating table. This is conside~ced a distinct disadvantage.
SUNEV1AR''Y' OF TTY INV'EN'TION
,Au object of the present invention is thus to fuzther develop a suitable unbalanced vibrator such that, to the greatest extent possible, these residual vibrations no longer occur. This object is achieved a.GCOrding to the invention in that the , unbalance shafts are the rotor shafts of the motors and the motors are mounted an the vibrating table.
The inwerrtitoz~ h,as the advaxxtage that the cardan sha.'fts that were conventional until now, by which the unbalance sh.a~fts were dxiven by motors that were firmly mounted on the bed of s stone forming machine, uncoupled from the vibrating table, can be o;rnitted in the machine of the invention. Their bearings can also be omitted. By the omission of these mechaniea.l components the vibrating device is more cost-effective and requires less maintenance. Also, the cardaa shafts and their bearings required a part of the driving power, so that by their omission the power requirement of the motors is reduced, because no unnecessary mechanism xnust be moved along.
With tht mcntioncd cardan shafts, bxause of the gimbal error, a slight irregularity always occurs between the drive and driven mcchaaisms of such a shaft. This irregularity is now avoided. Consequently, an acceleration and deceleration of the caxdan shaft resulting ~rozzz this izregulaxity, which eonsrtantly occurred until now and had caused a loading of the motors,, so that the motors were only accelerated or decelerated by performing an angular adjustment, are now eliminated.
1 S By the discontinuation of the co-rotating connection point the regulation of the rotational speed of the unbalance shafts carx also be done more quickly, since during this regulation a smaller inertia ofthe total, rotating masses acts in a positive way.
It is fimdanaentally advantageous if the motors with the unbalance shafts are each provided in pairs on the vibrating table. Each pair can thereby be arranged essentially symmetrically to the center of the vfbxating table, so that it then lies essentially in a bwrizoatal plate.
It is also possible, however, that each pair of motors be arranged essentially in a verxieal pl,~ae.
Because of the pair-wise arrangement, two motors can be provided to operate respectively with opposite rotation, so that f~'om these only one resulting unbalanced force at a time is generated in the essentially desired vertical direction. By the symmetrical arrangement of this pair, a point of application of these resulting vibrational forces is thereby ensured to be as centered as possible.
-z-It should also be mentioned that, not only can all of the symmetrically arranged pairs lie in one plane, but they can also be arranged in their own horizontal or ~rertical plane independently of the other pairs_ xn order that the total center of gravity of the vibrating table, due to the motors with unbalanced weights mounted on it, nvt be positioned too far away from the plane in which the resulting vibration forrx acts, it is proposed that the unbalat~e shafts be the rotor shafts of the motor, and pmject from the motors at their two ends; wherein they are each provided there with an unbalanced weight that acts in the same direction_ External unbalance sbsfts are thereby also no longer necessary, so that by their omission and by omission of their bearings the power consumption of the motors is in tuna reduced, and the regulation can occur faster.
For rapid regulation of the unbalanced masses the motoi5 are provided with a rotor position detection, which sends its results~immediately to the control device. This rotor position detection can involve sine-coszue transnnitters, for example, I 5 having a considerably higher resolution than that o~ conventional increment transmitters. For coaespondingly demanding regulation tasks, one obtains such sine-cosine transmitters haviu~g zesolutions that are over 65,000 ipcrements per revolution.
Thus, even the smallest regulation deviations son be detested and can be immediately counterbalanced because of the good dynamics of tl~e proposed vibra~ng table.
Zp Also, a so-called z'esolver, which is mounted on one end of the shaft ~d generates a voltage which is a function of the rotational position and which has a sinusoidal progression when the shaft rotates, can be used, wherein it is also essential here that the clectroniGS of the regulator are able to evaluate a resolution of greater than or equal to 65,000 increments per revolution.
25 It is also essential in terms of the co~atrol, that one motor represents the master drive, while the other motors are designed to be slave drives.
The motom are thus controlled in rotational speed and power output via frequency con~vexters, which are simultaneously cold as position wntrollers. A
phase angle of 180° between the unbalanced masses can thereby be obtained by an 30 adjustment ofthe two motor pairs by +90° or 90°.
_3..
rt should be mentioned here that the motors are only coupled together via electronic components, frequency converters with synchronization control, so that no additional mechanisms, such as. toothed belts, gears, etc. are necessary.
The frequency converters therein are in addition so coupled together that angular deviations between the motors due to signal runtimes can be avoided.
In particular, the roaster axle passes on its position information directly to the motor allocated to the master drive and conning synalazonously in a first pair. In addition, the master drive passes on its position to one of the other motors, which is made to follow synchronously in connection with the angular information additionally trausrruitted to it Z 0 from the control. This synchronously following motor thereby passes on its position information in turn to the motor in this seco~ad pair, synchronously following and allocated to it.
In a preferred embodiment, each motor is designed as a slave drive, and a virh~al master drive is used which contains the rotational, speed target value of the overriding control. The virtual master drive passes the rotational speed and the rotor position on to all slave drives. This improves even further the regulation characteristics and also the interchaageability of the electronic controllers.
BRIEF DESCRIPTION FO THE SEVERAL VIEWS OF 'THE DRAW1NG8 the foregoing summary, as weh as the following detailed description of the invention, will be better understood w'hezr read in conjunction witlx the appended drawings. For tl~e purpose of illustrating the invention, there are show~zt in the drawings embodi~naent(s) which are presently preferred. It should be understood, howevex, that the invention is not limited to the precise arrangements and insttumeo~.talities shown. Ia the drawings:
Fig. 1 is a schematic side view of an unbalanced, vibrator according to the invention;
Fig. 2 is g schematic bottom view of the unbalanced vibrator of Fig. 1;
Fig. 3 is a schematic circuit diagram of the motors of the unbalanced vibrator; and _q,.
Ir ig. 4 is a schematic circuit diagram of the motors of an unbalanced vibrator according to another embodiment.
DETAILED DESCRIPTION OF THE INVENTION
In Fig. 1 one recognizes the vibrating table 1 of an unbalanced vibzator, which is installed in a stone forming machine for compacting coz~czete ele~oa,ez~ts, especially paving stones. With this vibrating table eonG2ete elements set on its uppex side'are thereby vibrated and thus compacted In order to vibrate or to create vibration, foux ttxxbalaaoee shafts 2 to 5 ate provided on the underside of the vibrating table 1. These unbalance shafts 2 to 5carry respective unbalance weights 6 to 9 an their outer ends.
As can be recognized in Fig. 1, these unbalance shafts with unbalance weights are provided respectively in pairs, namely in an outer pair consisting of the unbalance shafts 2 and 5 and an inner pair consisting of the unbalance shafts 3 and 4.
These unbalance shafts rotate respectively in pairs with the same rotational speed in opposite directions according to the arrows 10. Each individual pair of unbalance shafts 3, 4 and 2, 5 in total thereby generates only ozte vibration component in the vertical direction, since each pair rotates in phase-synchronization.
The resulting vibrating force, which results from the interference of the v'brating forces ofthe i~ividual unbslance~shaft pairs, can thus be varied between a maximum value and a u~nuxn value, in which the vibrating forces of the i~adividual pairs are brought into phase (~.axim~waa resulting vibrating force) oar into antiphase (minimum resulting vibzatittg force = 0).
In the example represented is Fig. 1 - assuming the same rotational 2S speed for all uztbalance shafts - exactly the smallest resulting vib~a~ing force is prevalent, since the individual vibrating forces directly offset each other.
In addition, ozte recognizes that the individual pairs are arranged symmetrically to the center pla~t~e 11 of the vibrating table, so that the vibrating force generated by each pair of unbalance shafts acts in this plane because of the unbalanced mass.
,5-In Fig. 2, the bottom view of the vibrating table 1 is represented.
One recognizes that the unbalance shafts 2 to 5 are the rotor shafts of motors 12 to 15 and that the unbalance shafts 2 to 5 project &ozn these motors.12 to 15 at their two ends. One recognizes further that on both ends of the unbalance shags 2 to 5, unbalance weights 6 to 9 directed in the same direction are Qrovided, so that each individual motor is also syu~metA-ical relative to the second central place 16 of the vibrating table 1 running transverse to the central plane 11. Consequently, it is also achieved that, relative to this central plane, a symmetrically acting force is present and thus, tbu resulting vibrating fvrcc can bo assumed to ba acting at tlxe iudttrsc~.ioz~, point 17 of the two central planes 11 and 16.
The motors 12 to 15 themselves have a rotor position detection and are, in particular, provided with resolvers, not shown, by which this detection can be carried out very precisely. The motor 12 'thereby fvnetiozts as a coaster dxiwe, while the motors 13, 14, and 15 are designed as slave drives.
Thus, the motor 15 always rotates in the opposite direction synchronously with the motor 12, while the motozs 13 and 14 are each regvLated as necessary, in order to amplify or reduce the result~ung vibrating force. The motors 13, 14 in turn each rotate synchronously in opposite directions. .
All motors are electric asynchronous ~trtachines, which optionally can also be operated in emergency operation on the standard power network. It is essential that the motors arc only connected to each other via electronic components, while no mechanical components, which entail additional wexgb~t, are present.
This electronic connection is represented in Fig. 3. To the motors 12, 13, 14, 15, for their rotational speed and power control, are pre-eonaected frequency 2S converters 18, 19, 20, and 21, which get power from the standard power network 22.
herein, a rotational speed target value 24 is provided to the frequency converter 18 from an overriding wntsol 23.
The rotational speed and rotational position resulting from tk~is are passed on from the frequency converter 18, allocated to the master drive 12, to the frequency converters 19 and 21 via the communication lines 25. The freque~o~cy converter 21 thereby ensures that the motor 15 rotates at the same rotational speed, but in the opposite direction, synchronously with the master motor 12.
Opposed to this, another angular target value 26 is supplied to the frequency converter 19 via the overriding control 23, from which a phase difference to the master drive 12 results for the motor 13. The frequency converter 19 thus passes on its rotational speed and rotational position via the connection lxn~e 27 to the frequency converter 20, by which the motor 14 is operated synchronously, but diametrically opposed, with tlae motor 13.
By this direct coupling of the &equ~cncy conYUtcrs 18, 19, 20 and 21 among eacb, other, short signal run times are achieved, so that no angular deviations occur between the motors, and the combined motor pairs 12 and 15 or 13 and 14 each rotate synchronously. 'this dece~at~ral,~ized cozrtxol in the frequency converters is thus quicker than it could be done with the centralized design.in the overriding control 23.
An alternative electronic connection is represented izt Fig. 4. To the motors 12, 13, 14, 1 S, for their rotational speed and power control, axe again pre-connected frequency conv~eztezs 18, 19, 20, and 21, which get power from the standard power network 22. Herein, however, a rotational speed target value 24 is now provided from an overriding control 23 to a. virtual master drive 28.
The rotational speed and rotational position resulting from this are passed on from this virtual master drive 28 via the cocamunication lines 25 to the allocated frequency converters 18,19, 20 and 21, which thus function es slave drives for the virtual master drive 28. The virtual master drive 28, which acts as a correspondingly programmed control element that simulates a motor, now provides the rotational speed and rotor position to the motors 12, 13,14 and 15 vxa the frequency converters 18, 19, 20 and 21. Altenzatively, the frequency converters 20 and 21 ezxsure that the motors 14 and 15 rotate with the sarl~e rotational speed, but in the opposite direction, synchronously with the motors 12 and 13.
In this circuit a further improvement of 'the control properties is achieved, and the iuaterck~angeability of the electronic regulators and frequency converters 18, 19, 20 and 21 is also improved.
In this circuit another angular target value 26 is given tn the frequency converters 19 and 20 via the overriding control 23, from which the phase difference for the paotors 13 and 14 to the motors 12 and 15 results.
It will be appreciated by those stalled in the art that changes could be S made to the embodiments) described above without departing from the bxoad inventive concept thereof. It is understood, therefore, that this invention is not limited to the garticular ~embodiment(s) disclosed, but it is intended to covey modifications within the spirit aad scope of the present iu~~'ez~txoz~ as defined by the appended claims.
_g..
Unbalanced Vibrator For Stone Forming Macbanes BACKGROUND OF THE INVENTION
Tlxe invention relates to as unbalanced vibrator for compa,cti.ag cozrcxete components, in particular paving stones during their manufacture, the vibrator bring built into a stone forming machine. An unbalanced vibrator of this type usually has a vibrating table, on which unbalance shafts are arranged, which are driven by at least one motor, wherein a device is provided for control and/or regulation of the rotational speed or relative phase. position of the unbalance shags. A device of this type is lrnown, for example, fmm German Utility Model DE-U-29712 242_ In unbalance vibrators of this type the vibrating direction and amplitude are set via the phase position of several unbalanced masses relative to each other, wherein a correspoodi~otg regulation can lead to the forces generated by the unbalanced masses on the vibrating table becoming offset, and consequently the vibzatyx~,g table remains at rest.
However, even a slight offset angle among the unbalance shafts in their "neutral positiozr'' Ieads to a relatively stmng undesired residual vibration or oscillation of the vibrating table. This is conside~ced a distinct disadvantage.
SUNEV1AR''Y' OF TTY INV'EN'TION
,Au object of the present invention is thus to fuzther develop a suitable unbalanced vibrator such that, to the greatest extent possible, these residual vibrations no longer occur. This object is achieved a.GCOrding to the invention in that the , unbalance shafts are the rotor shafts of the motors and the motors are mounted an the vibrating table.
The inwerrtitoz~ h,as the advaxxtage that the cardan sha.'fts that were conventional until now, by which the unbalance sh.a~fts were dxiven by motors that were firmly mounted on the bed of s stone forming machine, uncoupled from the vibrating table, can be o;rnitted in the machine of the invention. Their bearings can also be omitted. By the omission of these mechaniea.l components the vibrating device is more cost-effective and requires less maintenance. Also, the cardaa shafts and their bearings required a part of the driving power, so that by their omission the power requirement of the motors is reduced, because no unnecessary mechanism xnust be moved along.
With tht mcntioncd cardan shafts, bxause of the gimbal error, a slight irregularity always occurs between the drive and driven mcchaaisms of such a shaft. This irregularity is now avoided. Consequently, an acceleration and deceleration of the caxdan shaft resulting ~rozzz this izregulaxity, which eonsrtantly occurred until now and had caused a loading of the motors,, so that the motors were only accelerated or decelerated by performing an angular adjustment, are now eliminated.
1 S By the discontinuation of the co-rotating connection point the regulation of the rotational speed of the unbalance shafts carx also be done more quickly, since during this regulation a smaller inertia ofthe total, rotating masses acts in a positive way.
It is fimdanaentally advantageous if the motors with the unbalance shafts are each provided in pairs on the vibrating table. Each pair can thereby be arranged essentially symmetrically to the center of the vfbxating table, so that it then lies essentially in a bwrizoatal plate.
It is also possible, however, that each pair of motors be arranged essentially in a verxieal pl,~ae.
Because of the pair-wise arrangement, two motors can be provided to operate respectively with opposite rotation, so that f~'om these only one resulting unbalanced force at a time is generated in the essentially desired vertical direction. By the symmetrical arrangement of this pair, a point of application of these resulting vibrational forces is thereby ensured to be as centered as possible.
-z-It should also be mentioned that, not only can all of the symmetrically arranged pairs lie in one plane, but they can also be arranged in their own horizontal or ~rertical plane independently of the other pairs_ xn order that the total center of gravity of the vibrating table, due to the motors with unbalanced weights mounted on it, nvt be positioned too far away from the plane in which the resulting vibration forrx acts, it is proposed that the unbalat~e shafts be the rotor shafts of the motor, and pmject from the motors at their two ends; wherein they are each provided there with an unbalanced weight that acts in the same direction_ External unbalance sbsfts are thereby also no longer necessary, so that by their omission and by omission of their bearings the power consumption of the motors is in tuna reduced, and the regulation can occur faster.
For rapid regulation of the unbalanced masses the motoi5 are provided with a rotor position detection, which sends its results~immediately to the control device. This rotor position detection can involve sine-coszue transnnitters, for example, I 5 having a considerably higher resolution than that o~ conventional increment transmitters. For coaespondingly demanding regulation tasks, one obtains such sine-cosine transmitters haviu~g zesolutions that are over 65,000 ipcrements per revolution.
Thus, even the smallest regulation deviations son be detested and can be immediately counterbalanced because of the good dynamics of tl~e proposed vibra~ng table.
Zp Also, a so-called z'esolver, which is mounted on one end of the shaft ~d generates a voltage which is a function of the rotational position and which has a sinusoidal progression when the shaft rotates, can be used, wherein it is also essential here that the clectroniGS of the regulator are able to evaluate a resolution of greater than or equal to 65,000 increments per revolution.
25 It is also essential in terms of the co~atrol, that one motor represents the master drive, while the other motors are designed to be slave drives.
The motom are thus controlled in rotational speed and power output via frequency con~vexters, which are simultaneously cold as position wntrollers. A
phase angle of 180° between the unbalanced masses can thereby be obtained by an 30 adjustment ofthe two motor pairs by +90° or 90°.
_3..
rt should be mentioned here that the motors are only coupled together via electronic components, frequency converters with synchronization control, so that no additional mechanisms, such as. toothed belts, gears, etc. are necessary.
The frequency converters therein are in addition so coupled together that angular deviations between the motors due to signal runtimes can be avoided.
In particular, the roaster axle passes on its position information directly to the motor allocated to the master drive and conning synalazonously in a first pair. In addition, the master drive passes on its position to one of the other motors, which is made to follow synchronously in connection with the angular information additionally trausrruitted to it Z 0 from the control. This synchronously following motor thereby passes on its position information in turn to the motor in this seco~ad pair, synchronously following and allocated to it.
In a preferred embodiment, each motor is designed as a slave drive, and a virh~al master drive is used which contains the rotational, speed target value of the overriding control. The virtual master drive passes the rotational speed and the rotor position on to all slave drives. This improves even further the regulation characteristics and also the interchaageability of the electronic controllers.
BRIEF DESCRIPTION FO THE SEVERAL VIEWS OF 'THE DRAW1NG8 the foregoing summary, as weh as the following detailed description of the invention, will be better understood w'hezr read in conjunction witlx the appended drawings. For tl~e purpose of illustrating the invention, there are show~zt in the drawings embodi~naent(s) which are presently preferred. It should be understood, howevex, that the invention is not limited to the precise arrangements and insttumeo~.talities shown. Ia the drawings:
Fig. 1 is a schematic side view of an unbalanced, vibrator according to the invention;
Fig. 2 is g schematic bottom view of the unbalanced vibrator of Fig. 1;
Fig. 3 is a schematic circuit diagram of the motors of the unbalanced vibrator; and _q,.
Ir ig. 4 is a schematic circuit diagram of the motors of an unbalanced vibrator according to another embodiment.
DETAILED DESCRIPTION OF THE INVENTION
In Fig. 1 one recognizes the vibrating table 1 of an unbalanced vibzator, which is installed in a stone forming machine for compacting coz~czete ele~oa,ez~ts, especially paving stones. With this vibrating table eonG2ete elements set on its uppex side'are thereby vibrated and thus compacted In order to vibrate or to create vibration, foux ttxxbalaaoee shafts 2 to 5 ate provided on the underside of the vibrating table 1. These unbalance shafts 2 to 5carry respective unbalance weights 6 to 9 an their outer ends.
As can be recognized in Fig. 1, these unbalance shafts with unbalance weights are provided respectively in pairs, namely in an outer pair consisting of the unbalance shafts 2 and 5 and an inner pair consisting of the unbalance shafts 3 and 4.
These unbalance shafts rotate respectively in pairs with the same rotational speed in opposite directions according to the arrows 10. Each individual pair of unbalance shafts 3, 4 and 2, 5 in total thereby generates only ozte vibration component in the vertical direction, since each pair rotates in phase-synchronization.
The resulting vibrating force, which results from the interference of the v'brating forces ofthe i~ividual unbslance~shaft pairs, can thus be varied between a maximum value and a u~nuxn value, in which the vibrating forces of the i~adividual pairs are brought into phase (~.axim~waa resulting vibrating force) oar into antiphase (minimum resulting vibzatittg force = 0).
In the example represented is Fig. 1 - assuming the same rotational 2S speed for all uztbalance shafts - exactly the smallest resulting vib~a~ing force is prevalent, since the individual vibrating forces directly offset each other.
In addition, ozte recognizes that the individual pairs are arranged symmetrically to the center pla~t~e 11 of the vibrating table, so that the vibrating force generated by each pair of unbalance shafts acts in this plane because of the unbalanced mass.
,5-In Fig. 2, the bottom view of the vibrating table 1 is represented.
One recognizes that the unbalance shafts 2 to 5 are the rotor shafts of motors 12 to 15 and that the unbalance shafts 2 to 5 project &ozn these motors.12 to 15 at their two ends. One recognizes further that on both ends of the unbalance shags 2 to 5, unbalance weights 6 to 9 directed in the same direction are Qrovided, so that each individual motor is also syu~metA-ical relative to the second central place 16 of the vibrating table 1 running transverse to the central plane 11. Consequently, it is also achieved that, relative to this central plane, a symmetrically acting force is present and thus, tbu resulting vibrating fvrcc can bo assumed to ba acting at tlxe iudttrsc~.ioz~, point 17 of the two central planes 11 and 16.
The motors 12 to 15 themselves have a rotor position detection and are, in particular, provided with resolvers, not shown, by which this detection can be carried out very precisely. The motor 12 'thereby fvnetiozts as a coaster dxiwe, while the motors 13, 14, and 15 are designed as slave drives.
Thus, the motor 15 always rotates in the opposite direction synchronously with the motor 12, while the motozs 13 and 14 are each regvLated as necessary, in order to amplify or reduce the result~ung vibrating force. The motors 13, 14 in turn each rotate synchronously in opposite directions. .
All motors are electric asynchronous ~trtachines, which optionally can also be operated in emergency operation on the standard power network. It is essential that the motors arc only connected to each other via electronic components, while no mechanical components, which entail additional wexgb~t, are present.
This electronic connection is represented in Fig. 3. To the motors 12, 13, 14, 15, for their rotational speed and power control, are pre-eonaected frequency 2S converters 18, 19, 20, and 21, which get power from the standard power network 22.
herein, a rotational speed target value 24 is provided to the frequency converter 18 from an overriding wntsol 23.
The rotational speed and rotational position resulting from tk~is are passed on from the frequency converter 18, allocated to the master drive 12, to the frequency converters 19 and 21 via the communication lines 25. The freque~o~cy converter 21 thereby ensures that the motor 15 rotates at the same rotational speed, but in the opposite direction, synchronously with the master motor 12.
Opposed to this, another angular target value 26 is supplied to the frequency converter 19 via the overriding control 23, from which a phase difference to the master drive 12 results for the motor 13. The frequency converter 19 thus passes on its rotational speed and rotational position via the connection lxn~e 27 to the frequency converter 20, by which the motor 14 is operated synchronously, but diametrically opposed, with tlae motor 13.
By this direct coupling of the &equ~cncy conYUtcrs 18, 19, 20 and 21 among eacb, other, short signal run times are achieved, so that no angular deviations occur between the motors, and the combined motor pairs 12 and 15 or 13 and 14 each rotate synchronously. 'this dece~at~ral,~ized cozrtxol in the frequency converters is thus quicker than it could be done with the centralized design.in the overriding control 23.
An alternative electronic connection is represented izt Fig. 4. To the motors 12, 13, 14, 1 S, for their rotational speed and power control, axe again pre-connected frequency conv~eztezs 18, 19, 20, and 21, which get power from the standard power network 22. Herein, however, a rotational speed target value 24 is now provided from an overriding control 23 to a. virtual master drive 28.
The rotational speed and rotational position resulting from this are passed on from this virtual master drive 28 via the cocamunication lines 25 to the allocated frequency converters 18,19, 20 and 21, which thus function es slave drives for the virtual master drive 28. The virtual master drive 28, which acts as a correspondingly programmed control element that simulates a motor, now provides the rotational speed and rotor position to the motors 12, 13,14 and 15 vxa the frequency converters 18, 19, 20 and 21. Altenzatively, the frequency converters 20 and 21 ezxsure that the motors 14 and 15 rotate with the sarl~e rotational speed, but in the opposite direction, synchronously with the motors 12 and 13.
In this circuit a further improvement of 'the control properties is achieved, and the iuaterck~angeability of the electronic regulators and frequency converters 18, 19, 20 and 21 is also improved.
In this circuit another angular target value 26 is given tn the frequency converters 19 and 20 via the overriding control 23, from which the phase difference for the paotors 13 and 14 to the motors 12 and 15 results.
It will be appreciated by those stalled in the art that changes could be S made to the embodiments) described above without departing from the bxoad inventive concept thereof. It is understood, therefore, that this invention is not limited to the garticular ~embodiment(s) disclosed, but it is intended to covey modifications within the spirit aad scope of the present iu~~'ez~txoz~ as defined by the appended claims.
_g..
Claims (7)
1. An unbalanced vibrator for compacting concrete components, in particular paving stones, during their manufacture, comprising a vibrating table (1), unbalance shafts (2, 3, 4, 5) arranged on the vibrating table, motors (12, 13, 14, 15) allocated to the unbalance shafts (2, 3, 4, 5) for driving the unbalance shafts (2, 3, 4, 5), and a device for control and/or regulation of rotational speed or relative phase position of the unbalance shafts (2, 3, 4, 5), wherein, the unbalance shafts (2, 3, 4, 5) are rotor shafts of the motors (12, 13, 14, 15), and the motors (12, 13, 14, 15) are mounted on the vibrating table (1).
2. The unbalanced vibrator according to claim 1, wherein the motors (12, 15; 13, 14) with the unbalance shafts (2, 5; 3, 4) are respectively provided in pairs on the vibrating table (1), and each pair is essentially arranged symmetrically to a center (17) of the vibrating table (1).
3. The unbalanced vibrator according to claim 1, wherein the unbalance shafts (2, 3, 4, 5) project from the motors (12, 13, 14, 15) at both of their ends, and each carries there as unbalanced weight (6, 7, 8, 9) acting in a same direction.
4. The unbalanced vibrator according to claim 1, wherein the motors (12, 13, 14, 15) have a rotor position detection.
5. The unbalanced vibrator according to claim 1, wherein one motor (12) is a master drive and other motors (13, 14,15) are designed as slave drives.
6. The unbalanced vibrator according to claim 1, wherein a virtual master drive (28) is provided, and the motors (12, 13, 14, 15) are designed as slave drives.
7. The unbalanced vibrator according to claim 1, wherein the motors (12, 13, 14, 15) are electric asynchronous machines.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19850351.2 | 1998-11-02 | ||
| DE1998150351 DE19850351A1 (en) | 1998-11-02 | 1998-11-02 | Unbalance shaker for stone molding machines |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2287851A1 true CA2287851A1 (en) | 2000-05-02 |
Family
ID=7886344
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA 2287851 Abandoned CA2287851A1 (en) | 1998-11-02 | 1999-11-01 | Unbalanced vibrator for stone forming machines |
Country Status (3)
| Country | Link |
|---|---|
| EP (1) | EP0999020A3 (en) |
| CA (1) | CA2287851A1 (en) |
| DE (1) | DE19850351A1 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2002038289A1 (en) * | 2000-11-12 | 2002-05-16 | GEDIB Ingenieurbüro und Innovationsberatung GmbH | Device for modulating the activation energy in mass-spring oscillators |
| DE10145825B4 (en) * | 2001-09-13 | 2005-11-17 | Institut für Fertigteiltechnik und Fertigbau Weimar e.V. | Arrangement for compaction and shaping of mixtures |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR1444020A (en) * | 1965-05-05 | 1966-07-01 | Mini Transporturilor Si | Shaking table |
| GB2103333A (en) * | 1981-08-03 | 1983-02-16 | Richard Peter Bernard Davis | Improvements in vibrators |
| EP0258171A3 (en) * | 1986-08-29 | 1990-01-17 | Alperin Technical Pty.Ltd | Composite article and method and apparatus for producing same |
| DE4116647C5 (en) * | 1991-05-22 | 2004-07-08 | Hess Maschinenfabrik Gmbh & Co. Kg | shaker |
| DE4315344A1 (en) * | 1993-05-08 | 1994-11-10 | Siegfried Gebhart | Apparatus for producing vibrations |
| US5606231A (en) * | 1993-12-04 | 1997-02-25 | Netter Gmbh | Vibrating table for masses to be compacted and a vibratory method of compaction for the compaction of concrete |
| DE29712242U1 (en) * | 1997-07-11 | 1997-09-18 | Lonz Industrieautomation GmbH, 65510 Hünstetten | Unbalance shaker |
| NL1008725C2 (en) * | 1998-03-27 | 1999-10-01 | Mason Europ B V | Compaction press for forming concrete blocks, etc. |
-
1998
- 1998-11-02 DE DE1998150351 patent/DE19850351A1/en not_active Withdrawn
-
1999
- 1999-10-27 EP EP99121397A patent/EP0999020A3/en not_active Withdrawn
- 1999-11-01 CA CA 2287851 patent/CA2287851A1/en not_active Abandoned
Also Published As
| Publication number | Publication date |
|---|---|
| EP0999020A3 (en) | 2002-05-29 |
| EP0999020A2 (en) | 2000-05-10 |
| DE19850351A1 (en) | 2000-05-04 |
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Legal Events
| Date | Code | Title | Description |
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| FZDE | Dead |