EP1076602A1 - Dispositif de reglage pour regler le moment statique resultant de generateurs de vibrations a balourd - Google Patents

Dispositif de reglage pour regler le moment statique resultant de generateurs de vibrations a balourd

Info

Publication number
EP1076602A1
EP1076602A1 EP99927723A EP99927723A EP1076602A1 EP 1076602 A1 EP1076602 A1 EP 1076602A1 EP 99927723 A EP99927723 A EP 99927723A EP 99927723 A EP99927723 A EP 99927723A EP 1076602 A1 EP1076602 A1 EP 1076602A1
Authority
EP
European Patent Office
Prior art keywords
type
torque
phase angle
partial
stop
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.)
Withdrawn
Application number
EP99927723A
Other languages
German (de)
English (en)
Inventor
Hubert Bald
Brigitte Ludwig
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Gedib Ingenieurbuero und Innovationsberatung GmbH
Original Assignee
Gedib Ingenieurbuero und Innovationsberatung GmbH
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
Publication date
Application filed by Gedib Ingenieurbuero und Innovationsberatung GmbH filed Critical Gedib Ingenieurbuero und Innovationsberatung GmbH
Publication of EP1076602A1 publication Critical patent/EP1076602A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • 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

Definitions

  • Adjustment device for adjusting the resulting static moment of unbalance vibrators
  • the invention relates to an adjusting device for adjusting the resulting static moment of unbalance vibrators for generating directional vibrations, which static moment is generated by at least two pairs of partial unbalance bodies that can be adjusted relative to one another by a relative angle of adjustment ⁇ .
  • a special type of adjusting device for unbalance vibrators for generating directional vibrations is described in document EP 0506722 B1, which is to be considered as part of the general prior art.
  • the terms of the partial unbalance bodies and the partial centrifugal forces (or partial centrifugal force vectors), the partial unbalance bodies of one type and the other, used in the cited publication have been simplified. as well as the "pair" of partial unbalance bodies.
  • phase angle ⁇ is theoretically defined between the partial centrifugal force vectors of the individual partial unbalance bodies of the one and the other type of a "pair" of partial unbalance bodies.
  • phase angle ß can also be defined between features (e.g. geometric features) of the partial unbalance bodies of a pair, provided the position of the center of gravity of the eccentric mass is known.
  • these average reaction torques MRQ [which in turn now represent a function of the phase angle ⁇ , that is to say: MRQ ( ⁇ )] at a set phase angle 0 ° ⁇ ⁇ 180 ° on the partial unbalance bodies of a pair in such a way that the reaction torques MRQ of one type want to accelerate the rotation of the partial unbalance bodies of the one type and that the reaction torques MRQ of the other type want to delay the partial unbalance body of the other type.
  • the present invention further relates specifically to that type of ramming vibrators which are adjustable with regard to their static moment and work with high working rotational frequencies and which are set up for a special operating mode such that when they are used the excitation from below the working rotational frequency fo of the vibrator lying resonance frequencies f R should be avoided.
  • two special resulting static moments can optionally be set by means of their control devices during the vibrator rotation (in addition to the setting of any resulting static moments): Setting a "minimum position" with a minimum resulting static moment for generation a vibration amplitude equal to zero and setting a "maximum position" with a maximum resulting static moment to generate a maximum vibration amplitude.
  • the mode of operation of the special mode of operation is as follows: adjustment of the phase angle when the vibrator is at a standstill to the minimum position. Run-up of the vibrator with the minimum position set to the working rotational frequency fo. Adjustment of the phase angle to the maximum position and implementation of the vibration work. Adjustment of the phase angle to the minimum position. Reduction of the vibrator rotation frequency from the working rotation frequency to zero with the minimum position maintained.
  • the special mode of operation described last is also to be cited below under the designation “resonance avoidance mode”
  • Two types of adjustable vibrators are known for carrying out an operating mode as described above.
  • One genus which is described, for example, in EP 0 473449 B1 or in EP 524 056 B1 works for the purpose of adjusting the phase angle with a mechanical superposition gear, by means of which there is always a torque-transmitting connection of the partial unbalance bodies of one type to the partial unbalance bodies of the other type via the superposition gear.
  • the phase angle is adjusted without a superposition gear, using adjusting motors, which can also be working motors.
  • the present invention is of the latter type, since the adjustment of the phase angle is also carried out with the inclusion of drive motors.
  • the vibrator presented in DE 44 39 170 A1 is a very specific way of generating a directed resultant centrifugal force, using at least 3 pairs of partial unbalance bodies with at least 6 individual partial unbalance bodies.
  • This configuration results in a number of still unknown physical effects for a vibrator that is adjustable with respect to the phase angle (as shown in DE 44 39 170 A1).
  • the behavior of this vibrator "with regard to the question of whether, and if so, with what effects reaction torques occur" (column 4, lines 36-38). How the regulation of the phase angle with such effects, especially in the range -90 ° ⁇ ⁇ + 90 °, could be dealt with is left open in the description.
  • phase angle open control circuit
  • This control would then, as is also indicated by the control line 80 which opens between the motors 40 and 42 connected in series, function in a special way, as described in the document DE 43 01 368 cited there (corresponding to WO94 / 01225).
  • This particular way also includes, inter alia, that an adjustment of the phase angle ⁇ is only possible in the range 90 ° ⁇ ⁇ 180 ° (according to the angle definition of the present invention).
  • a stop for limiting the phase angle ⁇ for the purpose of setting a minimum amplitude which is not to be undercut is provided in order to be able to prevent a further change in the phase angle by means of restraint in the event of a failure of the motor control. This happens because if a real zero amplitude was set, the rolling bearings of all unbalanced shafts would be damaged. However, this stop does not serve to maintain the phase angle ⁇ as a minimum position in the sense of the "resonance avoidance Operating mode "when the vibrator starts up from standstill to the working rotational frequency. There is also a stop for setting the maximum amplitude, but only in the event of failure of the normal control device for the phase angle ⁇ .
  • Such as. 1 shows that in the vibrator described there each partial unbalance body is to be driven by its own motor, two hydraulic motors belonging to different partial unbalanced bodies being connected in series. A very special control of the motors (with an open control circuit), which is only suitable for a series connection, is possible in order to change the phase angle.
  • This limitation of the phase angle is necessary here as a safety measure because no control with a closed control loop is provided for this vibrator, and because the range of a phase angle ⁇ 0 ° ⁇ ⁇ 90 ° (according to the angle definition of the present invention) is not a here controllable area and is therefore excluded [page 7, lines 1 to 21; Page 11, lines 9 to 21].
  • a further disadvantage is the fact that there is only a clear correlation between the actuating torques of the servomotors and the relative actuating angles ⁇ set thereby if the vibrator vibrates at a constant rotational frequency and with the output of a constant useful power. If the amount of one of the last-mentioned variables changes in a non-predetermined manner, as can occur when using ramming vibrators, the use of a control system is necessary for setting or maintaining a predetermined relative actuation angle ⁇ .
  • the effort is reduced in particular by dispensing with a closed control loop.
  • a reduction in the maximum motor load is achieved, which means that motors with smaller dimensions can be used.
  • the problem of the controllability of the phase angle in the range -90 ° ⁇ ⁇ + 90 ° is avoided.
  • An automatic mode of operation of the vibrator regardless of the set working frequency and output power can be guaranteed, without using a closed control loop for the phase angle ß.
  • the adjustment from a minimum position to a maximum position (and vice versa) can take place extremely quickly.
  • Open and closed circuits can be used with hydraulically operated motors. When using hydraulic motors that are not connected in series, there is no need to provide a special energy source for carrying out the angle adjustment.
  • FIGS. 1 to 4 the FIGS. 3 and 3 each containing two partial drawings to illustrate the different switching states of the hydraulic circuit before the adjustment and after the adjustment of the resulting static Moment from a minimum position to a maximum position. Show:
  • FIGS. 1a and 1b show the diagram of an exemplary embodiment with a pump and two motors, different motors being subjected to power when the vibrator is operated with different static moments.
  • FIG. 2a and 2b the schematic of an embodiment with a pump and two motors, the operation of the vibrator with different static
  • FIGS. 3a and 3b show the diagram of an exemplary embodiment with a pump and two motors connected in series, the power to be supplied to the vibrator being distributed to both motors when the vibrator is operated with different static moments.
  • FIGS. 4a and 4b show an exemplary embodiment with partial unbalance bodies of the first and second types arranged concentrically on an unbalanced shaft.
  • FIG. 4b shows, on a reduced scale, an incision marked with AA in FIG. 4a.
  • the invention represents the result of the consideration that, at least for use as ramming vibrators, a simpler and cheaper solution compared to the prior art is created by dispensing with the possibility of setting any predetermined phase angle ⁇ , and is limited to the possibility of setting a minimum position and a maximum position, with which over 90% of practical tasks can be carried out.
  • the simpler solution must also enable the "resonance avoidance mode" to be carried out, since it has been shown that adjustable vibrators are used primarily because of the latter property.
  • the adjustment of the phase angle ⁇ is made more difficult by the phenomenon of the reaction torques, which act in different ways on the partial unbalance bodies of different types.
  • the effect of the average reaction torques MRQ or the course of the motor torques ⁇ MD to be applied to compensate for the reaction torques MRQ on the partial unbalance bodies as a function of the phase angle ⁇ is illustrated clearly in FIG. 2 of WO97 / 19765.
  • the curves KA and KB here represent the motor torques .DELTA.MD, which are to be applied by the motors when the respective phase angle .beta. Is set and maintained by the action of a closed control loop.
  • the curve KA runs through the point K (instead of E) and the curve KB runs through the point K '(instead of E'), because the distances EK and E'-K 'are the proportional engine torques for the implementation of the (now represent deleted) useful work.
  • the maximum of curve KA is 90 ° and the minimum of curve KB is also 90 °.
  • the curve KB would correspond to the new definition in the range 0 ° to 180 ° of one that would come about by supe ⁇ onation of the (straight) curve K'-D "and the curve B'-H'-A * .
  • the angular position of a minimum position of a vibrator according to the present invention is 180 ° (new definition).
  • the example described also shows the following facts: Provided that a constant brake pressure is generated from the beginning of the adjustment to its end at the output of the motor M1, which brake pressure is also in a certain ratio to the excess kinetic energy of the system generated by the motor M2 together rotating parts, you need in any case a lower pressure than is necessary to drive the non-braked motor when making adjustments using a closed control loop.
  • the adjustment energy E A must be greater than when the vibrator is idling.
  • this requires that the energy converted when braking the motor M1 must be higher.
  • the braking energy is dosed by a suitable empirically found combination of braking time and braking pressure in such a way that all tasks occurring in practice are taken into account. This requirement alone makes it necessary to use a stop that defines the maximum position.
  • the maximum stop has a first meaning in that it defines the maximum position. Its second meaning is that with the use of one of the claims in claim 3 under feature b) means to maintain the maximum position, the partial unbalance bodies of different types of a pair can act almost like a single composite unbalance body. This has a dynamic favorable effect, in that under these conditions both composite unbalance bodies (both pairs) tend to self-synchronize in the oscillating state (as in the case of a two unbalance directional oscillator), which is known to the person skilled in the art. This property can be used particularly advantageously in an arrangement of the partial unbalance bodies of different types on a common axis of rotation, such that one can do without any positively synchronizing gearwheels.
  • switching on e.g. an adjusting brake torque acting on the partial unbalance bodies of one type
  • switching is derived from the overarching term "switching" of a torque.
  • Switching a torque in this context means that the function of a brake or acceleration actuator is activated without this activation being dependent on the output signal of a closed control circuit for regulating the phase angle ⁇ .
  • a "stop is produced dynamically” if the stop surfaces are brought towards one another by a relative movement of the partial unbalance bodies of different types, so that the relative movement is essentially ended by the stop impact and not by a control measure.
  • a vibrator is identified by 100 and the hydraulic circuit for operating the vibrator by 150.
  • the schematically illustrated vibrator 100 with two motors M1 and M2 is used in an identical manner in all partial drawings of FIGS. 1 to 3 and is therefore only described once with reference to FIG.
  • a circle 102 symbolizes a gear wheel that can be rotated and driven about an axis of rotation 104.
  • the filled-in small circle 108 schematically indicates the welding point of a partial unbalance body and the bar marked 106 symbolizes the lever arm of the welding point.
  • 106 and 108 together symbolize a partial unbalance body which can be rotated about the axis of rotation 104 and which at the same time represents a partial centrifugal force vector and a partial torque of the resulting static moment M R ⁇ > .
  • the features identified by 102, 106 and 108 together form a symbol which is used several times and which is identified overall by U1-1. Accordingly, a combination of characters, starting with the letter U, should always be summarized as follows: a partial unbalance body with the partial centrifugal force vector represented by the position of the bar (106) with respect to its direction and a gearwheel that is always connected to the partial unbalance body to transmit torque (102).
  • the directions of rotation and also the rotational speeds of the partial unbalance bodies of the first and second types are identified by the arrows ⁇ 1 and e> 2, respectively.
  • the partial unbalance bodies shown can be contained in different types of vibrators.
  • the partial unbalance bodies could be arranged on four separate axes of rotation arranged parallel to one another.
  • U1-1 and U1-2 could correspond to the partial unbalance bodies 107 and 108 of FIG. 1 and U2-1 and U2-2 to the partial unbalance bodies 104 and 105 of FIG. 1 and also that Develop the mode of action described there.
  • the partial unbalance bodies could e.g.
  • the part unbalance bodies which are characterized by the same type and are forcibly synchronized by gearwheels, always produce a resulting centrifugal force seen in vectorial terms in the vertical direction with constant amplitude.
  • the partial unbalance bodies of different types can be rotated relative to one another by a certain phase angle ⁇ , as a result of which the total centrifugal force vector which moves the vibrator results from the resulting centrifugal forces of the different types by superimposing them .
  • a phase angle of ⁇ 180 ° is set, which corresponds to a minimum position.
  • the second function of the stop clutch C is that it can transmit torques in the stop positions from one part of the unbalance body to the other, the direction of action of the torques being dependent on the stop position assumed.
  • the stop coupling C has special elements for carrying out these tasks: With the part unbalance body U1-2, a torque-transmitting part 110 is used, at the end of which there is a first stop lever 112. A torque transmitting part 118 is connected to the part unbalance body U2-2, at the end of which there is a stop crank 116.
  • the schematic representation in FIG. 1a means that the first stop lever 112 forms a stop contact with the stop crank 116 in such a way that a torque is transmitted from the first stop lever 112 to the stop crank 116.
  • a small partial view A1 is drawn to the left of the stop coupling C, which results when one looks in the direction of arrow A at the end of part 110.
  • the first stop lever 112 is symbolized by 112 'and the stop crank 116 is symbolized by 116'.
  • the arrow 120 is intended to show that the torque is transmitted from 112 'to 116'.
  • a second stop lever 114 is shown, which as well the first stop lever 112 is attached to the end of the torque transmitting part 110.
  • the second stop lever 114 forms a stop contact with the stop crank 116 in such a way that a torque is transmitted from the stop crank 116 to the second stop lever 114.
  • a small partial view A2 is drawn to the left of the stop coupling C, which results when one looks in the direction of arrow A at the end of part 110.
  • the second stop lever 114 is symbolized by 114 'and the stop crank 116 is symbolized by 116'.
  • the arrow 122 is intended to show that the torque is transmitted from 116 * to 114 '.
  • FIGS. 1 to 3 show (indicated by the drawing with broken lines) an assembly 124 which is to be used alternatively in order to implement stop functions as are also carried out by the stop coupling C. can.
  • the assembly 124 is described in more detail with reference to FIG. 1b:
  • the assembly 124 is driven on the one hand via the gear wheel 132 with the partial unbalance bodies of the second type U2-1 and U2-2 and on the other hand via the gear wheel 134 with the partial unbalance bodies of the first type U1- 1 and U1-2 connected.
  • the stop group 136 On the same axis of rotation 130 as that of the gear wheels, the stop group 136, which also rotates, is arranged.
  • the double arrow 138 is intended to symbolize that the stop group 136 allows a relative rotation of the gear wheels 132 and 134 until a double stop contained in the stop group is reached.
  • the partial unbalance bodies U1-1 and U1-2 are driven by a hydraulic motor M1, which transmits its torque to the gearwheel of the partial unbalance body U1-2 via a shaft 142 and a gearwheel 140.
  • the partial unbalance bodies U2-1 and U2-2 are driven by a hydraulic motor M2, which transmits its torque to the gearwheel of the partial unbalance body U2-2 via a shaft 146 and a gear 144.
  • the relative positions of the partial unbalanced bodies of a pair can also be changed during the rotation of the partial unbalanced bodies.
  • the adjustment from one position to the other can not only take place with the application of torques generated by motors, but can also take place through the action of such mass torques which are caused by dynamic inertial forces of the polar moments of inertia of those rotating with the said partial unbalance bodies Parts are created. If e.g. In FIG.
  • FIG. 1 The exploitation of the effect of the dynamically generated mass torques in FIG. 1 essentially takes place in that the motors M1 are temporarily hydraulically strongly be slowed down. This can be done with different measures, of which 3 different hydraulic measures according to the invention are explained in more detail in FIGS. 1 to 3.
  • the high hydraulic pressure that can be generated during the braking process is passed into the input line of the motor M2 and the dynamic mass torque acting on the partial unbalance bodies U2-1 and U2-2 is thus also generated by a motor-generated torque supports to achieve the angular adjustment with an even lower braking of the motor M1.
  • FIGS. 1 to 3 are supposed to be closed circuits; alternatively, open circuits could also be used in other circuit designs.
  • the circuits are self-explanatory for the person skilled in the art. Therefore, the description of the individual figures can be limited to special effects.
  • Sub-figures 1a, 2a and 3a that circuit is shown with which all the partial unbalance bodies could be brought to a constant working rotational frequency before the angle adjustment process.
  • Sub-figures 1b, 2b and 3b each show the circuit with which the adjustment process was started.
  • Figure 1b shows the situation at the start of the adjustment of the phase angle ⁇ .
  • the driving pressure at the input I of the motor M1 was switched off and at the output O of the motor M1 a braking pressure builds up, which is set by the pressure limiting valve PLV, via which the backflow from the motor M1 Pump P can flow again.
  • a connection can be made from line point 170 to line point 172, with which the high pressure generated at motor output O can be directed to input I of motor M2.
  • the minimum position can be maintained in any case by switching on a throttle element in the return line of the motor M2 (as shown in FIG. 2 with 200).
  • the switching element 200 could also be a motor (e.g. an axial piston motor) that can be changed in terms of its volumetric flow, the drive power of which could be fed back to the drive of the pump.
  • a motor e.g. an axial piston motor
  • FIG. 2b shows the situation at the start of the adjustment of the phase angle.
  • the driving pressure at the input I of the motor M1 was switched off and at the output O of the motor M1 a braking pressure builds up, which is set by the pressure relief valve PLV, via which the backflow from the motor M1 the pump P can flow again.
  • a connection can be made from line point 270 to line point 272, with which the high pressure generated at output O of motor M1 can be directed to input I of motor M2.
  • the valves V3 and V4 are switched back again.
  • Measures can be taken to ensure that the maximum position is adhered to, such as the use of a mechanical interlocking of two partial unbalanced bodies against one another, shown in FIG. 4, or the use of the effect of reversing the direction of the reaction torques MRQ when setting a maximum position with a phase angle ß ⁇ 0 ° (later called "over-adjustment").
  • both motors M1 and M2 can output their power in parallel.
  • the switching back of the phase angle ⁇ from the maximum position to the minimum position when the working rotational frequency is set can be done, for example, by briefly using the switching element 200 already mentioned.
  • the minimum position can be maintained in that the motor M2 develops a higher braking torque than the motor M1 by switching on the throttling switching element 200 .
  • the adjusting device according to FIG. 3 works with two successively connected hydraulic motors M1 and M2.
  • the hydraulic control 300 for the motors contains an electrical pressure control valve Vpc, which is fed by a special pressure source S and which can be set electrically to three different output pressures p ⁇ dj-i to p ⁇ dj-3.
  • the pressure control valve also has the property of being able to reduce a pressure at its outlet which is higher than the set pressure and is caused by a flow flowing backwards into the valve (and to a leakage drain).
  • the adjusting device can carry out the following procedure in several phases, from starting up the vibrator to stopping, starting with the positions 0 of the two
  • Valves V ⁇ and V6 Already in the process of leaving the vibrator at rest a minimum position is set at a rotational frequency lower than the working rotational frequency and then maintained. When the vibrator is at a standstill, all partial unbalanced masses are oriented downwards under the influence of gravitational acceleration.
  • the valve V5 in position 1 With a set small delivery volume of the pump P, the partial unbalance bodies U1-1 and U1-2 are first rotated by approximately 180 °, after which a switch back of the valve V5 to position 0 and at the same time an increase in the delivery volume Pump P takes place after a predetermined time ramp.
  • the motor M2 is dragged along without a pressure drop acting on it as the driving torque.
  • the phase angle ß is adjusted from the minimum position to the maximum position when the operating rotational frequency is set by applying an increased adjustment pressure (compared to the pressures present at the input of motor M2 during the minimum position) in position 1 of valve V6.
  • an increased adjustment pressure compared to the pressures present at the input of motor M2 during the minimum position
  • the partial unbalance bodies of the one type (U1-1, U1-2) adjusting braking torques and the partial unbalanced bodies of the other type have the effect of adjusting acceleration torques.
  • the maximum position reached is shown in Figure 3b.
  • the maximum position is secured against the influence of reset torques using the same principle that was used to set the maximum position.
  • position 1 of valve V6 at the input of motor M2 another special adjustment pressure pAdj, - 2 is applied , the level of which is sufficient to prevent resetting.
  • the level of the adjustment pressure P M - 2 is adapted to the operating situation using a special control algorithm for generating a variable control signal for the pressure control valve Vpc.
  • phase angle ß is reset from the maximum position to the minimum position when the working rotational frequency is set by briefly switching on the special adjustment pressure already mentioned with V6 in position 2 at the output of motor M2. This measure develops a braking torque on the M2 motor.
  • phase angle ß in the range 0 °
  • the minimum position is observed during the process of stopping the vibrator based on the working rotational frequency as follows: There is a reduction in the
  • valve V6 switches a low pressure p M i, -3 ⁇ Pcharg ⁇ to the input of motor M2.
  • the motor M2 is braked while the motor M1 tries to advance.
  • the special property of the pressure control valve Vpc ensures that 1
  • FIG. 4a shows a vertical section through the axis of rotation of the unbalanced shaft 400 shown, in which the partial unbalance bodies 403a and 403b follow an incision marked BB in FIG. 4b, while all other parts correspond to the incision marked CC in FIG. 4b.
  • the setting of the phase angle shown in FIG. 4a corresponds to a maximum position, in which, however, the possible mechanical locking of this position has not yet been switched on.
  • a vibrator can be operated with two versions.
  • the gearwheels 424 and 426 represented by dash-dot lines are in principle omitted, since synchronous guidance occurs automatically after the partial unbalance body is locked and can also be supported with other control means for the rotation angles of the motors known to the person skilled in the art.
  • version 2 described later the unbalanced shafts are driven according to a diagram shown in FIG. 2.
  • FIG. 4a shows: An unbalanced shaft 400 is mounted in a housing 402 by means of roller bearings 436 and 436 '. On the right side is the unbalanced shaft with a hole
  • a pressure fluid can be supplied both under pressure and can be returned without pressure.
  • a partial unbalance body of one type 401 is connected to the unbalanced shaft 400 in a torque-transmitting manner with the aid of two feather keys, while the two parts 403a and 403b of the partial unbalance body of another type, with the participation of the needle bearings 404 and 408, can be rotated relative to the unbalanced shaft.
  • a flange bushing 410 for receiving the gear 426 is also connected in a rotationally fixed manner to the unbalanced shaft 400 with the aid of a parallel key 422.
  • Part 403a which carries a second gear 424 on its left side, is connected to part 403b by means of a stop bolt 427, which is used both for transmitting a torque between the two parts and as a stop element for forming two stops for limiting
  • the two stops are formed when the stop bolt 427 contacts one of the two stop surfaces 428 and 430 (FIG. 4b), which stop surfaces are embodied on the partial unbalance body of the one type 401. As can be seen from Fig. 4b,
  • the other stop is formed, at which the stop bolt 427 (designated 427 'in this position) in
  • the partial unbalance bodies 401 and 403 can be fixed in their relative position both in the minimum position and in the maximum position with a switchable mechanical lock, with the participation of the three parts which can be axially displaced in their mounting holes: 5 driving pin 450, locking pin 452 and bush 454.
  • the locking is caused by the removal of the driving bolt 450 on its left side in the cylinder 466 which can be pressurized with the pressurized fluid, which thereby displaces the other two parts to the right until the bush 454 touches the bottom of its bore.
  • the locking is released by the fact that the pressure fluid on the left side of the driving pin 450 is depressurized, which enables the spring 456 to move all three parts back into the drawn starting position.
  • the locking function described can also take place if the partial unbalance body 401 is relative to the partial unbalance body
  • the 15 403 is moved from the maximum position shown by the adjustment angle ⁇ ß (e.g. 180 °) to the minimum position. After such an adjustment, the locking bolt 458 takes the place of the locking bolt 452, and vice versa.
  • ⁇ ß e.g. 180 °
  • the second unbalanced shaft 400 ' is constructed identically to the unbalanced shaft 400, but mirror-symmetrically to the axis of symmetry 460, and with a center distance such that the two gear wheels mesh with each other.
  • the center line 432 symbolizes the coaxial connection of the unbalanced shaft 400 with the motor M4 and the center line 432 'the coaxial connection of the unbalanced shaft 400' with the motor M5.
  • the diagram of the hydraulic circuit 462 shows that the 5 (equally large) motors M4 and M5 are connected in parallel to a pump P operated in a closed circuit.
  • the pump P can be variably adjusted with respect to the volume flow it pumps.
  • the adjustment angle ⁇ lying between the minimum position and the maximum position does not necessarily have to be 180 °.
  • a minimum position ß 180 °
  • an adjustment angle ⁇ ß> 180 ° with "over-adjustment” a maximum position can be achieved at a phase angle ß ⁇ 0 °, at which the reversed directions of action of the reaction torques MRQ results in an automatic compliance with the maximum position.
  • a maximum position is reached with a phase angle ß> 0 °. If this maximum position is not artificially fixed, the vibrator will automatically return to the minimum position due to the effect of the reaction torques MRQ.
  • the stops could also be equipped with damping functions.
  • the organs 480 and 480 'could for example, be pistons of hydraulic dampers which are arranged in the partial unbalance bodies 401 and 401' in a plane perpendicular to their axes of rotation.
  • the operating mode of a vibrator is as follows: When the vibrator is at a standstill, all of the unbalance bodies hang down and automatically form a maximum position when the lock is switched off. When the motors are started simultaneously by adjusting the volume flow of the pump P after a time ramp from zero after about half a turn (in the direction of the arrows ⁇ 1), the partial unbalance body 401, 401 '(only these are rotated first) ) reaches the minimum position (stop bolt 427 'on stop surface 430), which minimum position is maintained as a result of the developing acceleration-adjusting torque and, at higher speeds, as a result of the effort of self-adjustment to a minimum position even after the working rotational frequency has been reached.
  • the pump volume flow is briefly reduced by a switching operation on the pump, as a result of which an adjusting braking torque is briefly developed on the partial unbalance body 401.
  • the partial unbalance bodies 403, 403 Due to its polar moment of inertia, the partial unbalance bodies 403, 403 'overtake the partial unbalance bodies 401, 401' in the direction of arrow 464 and the stop (427 + 428) occurs when the maximum position is reached. Since a pressure fluid under pressure had already been loaded on its left side during the process of adjusting the angle of the driving bolts 450, the partial unbalance bodies are locked against one another immediately after the maximum position has been reached.
  • the reset from the maximum position to the minimum position is released by relieving the pressure in the cylinder space 466. Since a maximum position is assumed at a phase angle of ⁇ > 0 °, the pha is automatically reset immediately after unlocking due to the effect of the reaction torques MRQ - Senwinkel in the minimum position.
  • the resetting of the phase angle to the minimum position can alternatively be achieved by briefly increasing the volume flow of the pump P are effected, whereby an acceleration of the partial unbalance body 401, 401 'takes place, or alternatively can also be initiated when using at least the two gears 426 and 426' by briefly switching on a throttle element 470 in the feed line to the motor M4.
  • version 1 can also be operated with only a single motor.
  • Fig. 4a shows a maximum position corresponding to Fig. 2b.
  • the set amplitude again becomes a little smaller than the theoretically maximum possible amplitude, but after falling below the
  • curves ⁇ MD describe the useful torque required in each case on the motors, that the motor operated according to curve KA
  • an abrupt acceleration of one type of partial unbalanced body could also be carried out, with a dynamic mass torque being developed on the other type of partial unbalanced body on the other type of partial unbalance body could compensate for the adjustment-preventing reaction torques MRQ.
  • the phase angle ⁇ could be adjusted from a minimum position to a maximum position.
  • the direction of rotation of the partial unbalance bodies of a pair can be both in the same direction and in opposite directions, for example for the use of the assembly 124 to form a stop.
  • the adjusting device Since with the adjusting device according to the invention a very quick adjustment from the minimum position to the maximum position (and vice versa) is possible, it also makes sense to operate the vibrator intermittently, with the dwell times switched on in the minimum position. Since the power consumption is relatively low in the minimum position, there is an average lower power consumption for the vibrator during work. This enables the vibrator to be connected to lower power pump drive motors. As an area of application for the invention, not only ram vibrators come into question, but also other working machines such as earth-moving machines or vibrators for

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)

Abstract

L'invention concerne un dispositif de réglage pour un générateur de vibrations à balourd comportant au moins deux paires de corps à balourd partiels qui peuvent être entraînés de façon à tourner autour d'un axe associé et dont les vecteurs de force centrifuge partiels, additionnés de manière vectorielle, forment le vecteur de force centrifuge résultant. Le réglage s'effectue entre un moment de déséquilibre minimal résultant (amplitude d'oscillation minimale) et un moment de déséquilibre maximal résultant (amplitude d'oscillation maximale) sans position intermédiaire. Les deux angles de phase limites associés sont réglés au moyen de deux butées. Ce dispositif de réglage permet également une accélération et un arrêt du générateur de vibrations avec un moment de déséquilibre minimal réglé. Ce dispositif de réglage utilise au choix un ou deux moteurs d'entraînement pour régler l'angle de phase. Grâce à l'utilisation de butées pour le réglage de l'angle de phase, il n'est pas nécessaire d'avoir recours à des moyens de commande complexes, et il est possible d'obtenir une structure compacte. Ce dispositif est employé de préférence pour des engins de chantier et des machines pour matériaux de construction.
EP99927723A 1998-05-08 1999-05-04 Dispositif de reglage pour regler le moment statique resultant de generateurs de vibrations a balourd Withdrawn EP1076602A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19820670 1998-05-08
DE19820670 1998-05-08
PCT/DE1999/001348 WO1999058258A1 (fr) 1998-05-08 1999-05-04 Dispositif de reglage pour regler le moment statique resultant de generateurs de vibrations a balourd

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EP1076602A1 true EP1076602A1 (fr) 2001-02-21

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US (1) US6504278B1 (fr)
EP (1) EP1076602A1 (fr)
JP (1) JP2002514502A (fr)
DE (1) DE19920348A1 (fr)
WO (1) WO1999058258A1 (fr)

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JP2002514502A (ja) 2002-05-21
WO1999058258A1 (fr) 1999-11-18
DE19920348A1 (de) 2000-01-13
US6504278B1 (en) 2003-01-07

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