Classifications

• • E—FIXED CONSTRUCTIONS
  • E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
  • E01C—CONSTRUCTION OF, OR SURFACES FOR, ROADS, SPORTS GROUNDS, OR THE LIKE; MACHINES OR AUXILIARY TOOLS FOR CONSTRUCTION OR REPAIR
  • E01C19/00—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving
  • E01C19/22—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving for consolidating or finishing laid-down unset materials
  • E01C19/23—Rollers therefor; Such rollers usable also for compacting soil
  • E01C19/28—Vibrated rollers or rollers subjected to impacts, e.g. hammering blows
  • E01C19/286—Vibration or impact-imparting means; Arrangement, mounting or adjustment thereof; Construction or mounting of the rolling elements, transmission or drive thereto, e.g. to vibrator mounted inside the roll
• • 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

• the invention relates to a vibration system for an earth compacting machine with at least one roller with adjustable amplitude of vibrations.
• vibration rollers are used for subsoil compacting and are used e.g. for compacting of the freshly laid asphalt, soil, and other compactable materials.
• the vibration rollers are a design of the compacting mechanisms using at least one subsoil compacting rotary roller for the subsoil compacting by traversing on it. In this case the force acting on the contact surface of the roller with the subsoil is very important for a high-quality compacting.
• the vibration rollers are equipped with a vibration mechanism acting on the rotary roller.
• the vibration mechanisms comprise external and internal, eccentrically arranged weights arranged on a rotary shaft, which shaft is placed within the rotary roller, whereby roller vibrations are produced.
• the vast majority of the vibration rollers for the subsoil compacting uses a constantly set amplitude of vibrations.
• the vast majority of the compacting machines comprises two vibration rollers arranged one after the other, the necessity appeared to set the amplitudes of vibrations of the front and the rear rollers differently in such machines.
• the documents CS AO 184081 and CS 244465 disclosed a solution, which allows to set the amplitude of vibrations continuously.
• none of the solutions is used at present because they were very complex and expensive to produce.
• Development of solutions allowing to change the amplitude continued in the direction of the two-amplitude designs, which designs were substantially cheaper. Therefore, the so designed compacting machines allow selecting of the vibration amplitude from two values - a small one and a big one.
• the basic disadvantage of the two-amplitude vibrator is that it is necessary to switch off the vibrations at first, before switching from the big amplitude to the small one, because in this design a switch-over of a two-amplitude vibrator requires to change the rotation direction of the vibrator. This means to switch off one of the vibrations, and to switch on the other one.
• the vibration rollers uses the continuously adjustable amplitude.
• An example of a machine allowing continuous adjustment of the amplitude of vibrations of each roller independently, and thereby to react on the momentary situation is disclosed for example in the document EP0034914, the applicant of which is the Hyster Company.
• This patent describes a vibration mechanism formed by the first weight, eccentrically placed within the compacting roller, and a second eccentric weight, arranged as rotary within the first weight. Further, the vibration mechanism comprises the first shaft, which is connected to the first weight for its turning, and a second shaft, placed coaxially with the first shaft being in contact with it, formed by a helix and the corresponding cuts between the first shaft and the second weight.
• Patent US 6,769,838, the applicant of which is Caterpillar Inc., is also based on similar principle.
• This document discloses a vibration mechanism formed both by the inner eccentric weight arranged within the roller and the external eccentric weight, arranged coaxially rotationally around the inner one.
• the first, i.e. the inner weight is connected to the first shaft
• the second, i.e. the external weight is connected to the second hollow shaft, arranged coaxially around the first one.
• Both shafts are connected with a gearbox with planet pinions.
• this solution also brings about some disadvantages, such as the impossibility to use this solution for the divided runner, and also it is not possible to use it for the heavy earth compacting machines, especially with weight above 15 tonnes, where it is necessary to use four bearings for bearing of the vibrator, what this solution does not allow. From this follows the limited possibility of its utilization.
• the present invention provides a vibration system with the possibility of the continuous adjustment of the amplitude of vibrations from the minimal to the maximal required value entirely linearly by means of a spiral rod provided with two spirals in opposite directions. Thereby, the uplift of the spiral rod is shortened to one half.
• the spiral rod is placed in the gearbox with four gear toothed wheels arranged off the vibrator axis.
• the continual adjustment of the mutual positions of the two eccentric weights, i.e. eccentric with regard to the roller axis, is controlled by a hydraulic circle comprising a pump, a proportional distributor with a distributor PID controller and a linear hydraulic motor.
• the proportional distributor receives the required signal from a handheld actuator or automatically from the controlling unit.
• An advantage of the solution according to this invention is a low requirement on a construction space. Another advantage is that the vibration amplitude can be varied very quickly in relation to the current conditions. According to this invention a change in vibrations can be carried out either manually or automatically.
• An advantage of the earth compacting machine provided by a vibration system with continually variable amplitude according to this invention is exactly the possibility to equip the machine with a controlling unit, a part of which is, according to this advantageous embodiment, also a compaction meter.
• the controlling unit which is for example a computer, a processor, etc., connected to a compaction meter, can optimize the size of the vibrations of the roller/rollers, or other characteristics eventually.
• An advantage of the vibration system according to the present invention is that considering the fact that the earth compacting machine equipped with such vibration system does not have to alter the rotation direction of the eccentric weights causing the roller vibrations, so as it is in the case of the two-amplitude machines.
• the machine operates the whole time below the limit when uncontrollable vibrations start to emerge. Because of this, the machine is more efficient and compacts the whole area in higher quality, as well as it is much more convenient for operation.
• each runner can operate independently, according to the current conditions under the runner.
• An advantage of this solution is the broad scope of settings of characteristics, the possibility of their optimization by means of a control unit. By this a higher machine performance and compacting of higher quality are obtained, i.e. a higher quality of the work done in comparison to the two-amplitude solution.
• a lower number of parts is used: only 4 gearwheels with oblique toothing, a spiral rod with two toothings and 2 spiral hubs, or even only a spiral rod with two toothings and 2 spiral hubs;
• an earth compacting machine equipped with a vibration system with an adjustment and/or control unit for controlling of vibrations is presented.
• Fig. 1 shows in cross-section made vertically in the axis plane a view of an embodiment of a vibration system with an undivided roller, e.g. for an earth compacting machine.
• Fig. 2 shows a complete side view of a roller of a vibration system by the vibration device of Fig. 1.
• Fig. 3 shows a detail of a gearbox in a cut-out of the view of the roller in Fig. 1 in a cross- section made in the plane marked as A-A in the Fig. 2.
• Fig.4 shows the same detail of the cut-out of the view on the roller in Fig. 1 , so as in Fig. 2, but in cross-section made in the plane marked as B-B in Fig. 2.
• Fig. 5 shows the second embodiment of the roller with divided runner, comprising the vibration device according to the present invention.
• Fig. 6 shows enlarged detail of the gearbox, designated as Area A in Fig. 5.
• Fig. 7 shows a view of the embodiment shown in Fig. 1 in cross-section C-C and shows the angle a of the shift of both weights.
• the roller which can be called also the vibration roller, comprises an undivided runner 30 having in its axes placed a vibration mechanism 9, a gearbox 21 and a motor 29.
• the motor 29 is firmly attached to the gearbox 2J .
• which gearbox 21 is rotationally connected with the runner 30 of the roller via a bearing 32.
• the vibration mechanism 9 is rotationally positioned in the runner 30, and is formed by the first eccentric weight J_0 and the second eccentric weight JJ_, which weights are arranged rotationally within the roller, and they are angularly shiftable, whereby they allow to vary the size of the vibration roller.
• the first eccentric weight J_0 and the second eccentric weight JJ_ which weights are arranged rotationally within the roller, and they are angularly shiftable, whereby they allow to vary the size of the vibration roller.
• the second eccentric weight 11 is arranged as internal and is rotationally supported on bearings 13 in the roller axis, and it is substantially directly connected by a shaft 12 to the motor 29 for its direct rotation by this motor.
• the first eccentric weight 10 is arranged rotationally supported on bearings 3J_ outside the second eccentric weight 1_1 and is connected to the motor 29 via a spiral rod 17 and the relevant transmissions, via which the driving force of the motor 29 is transmitted on this weight, i.e. the second eccentric weight 1_1 is driven by the driving motor 29 indirectly.
• the gearbox 21 comprises two pairs of gearwheels, the first pair of gearwheels 1, 2 and the second pair of gearwheels 3, 4.
• the toothed sleeves 7 and 8 with internal spiral toothings are firmly placed in the toothed wheels 2 and 3.
• the spiral rod ⁇ 7 which will be described in more detail later, is slidingly arranged in the sleeves 7 and 8 with spiral toothing.
• the toothed spiral rod 17 is adapted to transfer torque moment from the sleeve 7 to the sleeve 8 and is axially shiftable to them.
• the spiral rod 17 is connected to the linear hydraulic motor 26 via a thrust bearing 6.
• the motor 29, which is preferably a rotational hydraulic motor, is placed on the gearbox 21 and is connected via a shaft J_2 with the other eccentric weight ⁇ . to drive it.
• the motor 29 is also connected with the gearwheel i via a conical toothed clutch 5, which gearwheel ⁇ meshes with the gearwheel 2, in which gearwheel 2 the sleeve 7 with spiral toothing is firmly placed.
• the spiral toothing of the sleeve 8, which sleeve 8 is firmly placed in the gearwheel 3 is provided with a spiral toothing of the opposite direction than what is that of the spiral toothing of the sleeve 7.
• the spiral rod ⁇ 7 is provided both with the first spiral toothing 1_5 and the second spiral toothing 16. Both spiral toothings 1_5 and 16 exhibit mutually opposite direction of the spirals.
• the first spiral toothing 15 is right-handed and the other spiral toothing 16 is left-handed. Both spiral toothings are formed together with the corresponding toothings in sleeves 7 and 8 slidingly to allow mutual swivelling of both sleeves 7 a 8 to each other during shifting of the spiral rod sleeves 7 and 8.
• the sleeve 8 is provided with a left-hand spiral toothing inside, with which toothing it meshes the left-handed second spiral toothing 16 of the spiral rod ]_7, whilst the right-handed first spiral toothing 15 of the spiral rode ⁇ 7 meshes with the right-handed spiral toothing of the sleeve 7.
• the gearwheel 3 meshes with the gearwheel 4, which gearwheel 4 is firmly connected with the first eccentric weight 1 by a hollow shaft 18.
• Shifting of the spiral rod 17 is provided by a linear hydraulic motor 26 connected with the spiral rod ⁇ 7 with the help of a thrust bearing 6.
• the piston 27 of the linear hydraulic motor 26 is secured against swivelling by an axially arranged sliding rod 34.
• the sliding rod 34 prevents swivelling of the piston 27, and in case of the identical axial shift of the piston 27 and the sliding rod 34 the thrust bearing 6 allows rotation of the spiral rod ⁇ 7.
• the actuator 24 manually, or eventually by the controlling unit 19 automatically ⁇
• the information from the actuator 24 or the controlling unit 19 enters the evaluating controller device 23 ⁇ where the size of vibrations, given by the actual position of the first eccentric weight 10 with regard to the second eccentric weight ⁇ . , is evaluated.
• this position is found easily by means of a linear sensor 28, which sensor 28 is adopted for sensing the actual position of the spiral rod 17.
• the evaluating controller device 23 calculates the required size of vibrations and adjusts the proportional distributor 22 controlling the oil quantity delivered into the linear hydraulic motor 26 for adjusting the shift of the spiral rod ⁇ 7 to the required position.
• the oil who has passed the distributor 22 and the hydraulic hoses 25 into the linear hydraulic motor 26 moves its piston 27 into the required position, which was determined by the actuator 2 , or the control unit.
• the control unit 19 controlling the size of vibrations can be connected e.g. to the sensors monitoring the material compaction, the sensors for monitoring of the machine vibrations, etc.
• Controlling of vibrations by means of the control unit is sufficiently known from the state of the art, and will not be discussed any more in detail here. Important is only the fact that the vibration system according to the invention is particularly advantageous for using the possibility of automatic adjusting of the size of vibrations in relation to the measured characteristics. Types of the measured characteristics and the method of their measuring are not subject of this application. Substantial is that thanks to the linear change in adjustments of both eccentric weights, which change is not dependent on wear or on other operational causes, in the subject of the invention it is possible to obtain entirely reliable information on actual adjustment and on the necessary change, which was determined by the control unit on the basis of the measured characteristics or for example by the operator on the basis of his feelings and/or according to the current need.
• the basic angle a Before the first use or after the total repair it is necessary to set the basic angle a, between the first eccentric weight and the second one and this angle will be saved in the control unit as the basic reference value.
• This setting will be carried out by releasing the conical coupling 5, which will be released with regard to the position of the_gearwheel L
• the first eccentric weight 10 can be swivelled independently of the second eccentric weight IT , and it is possible to modify the setting of the basic angle a, which setting is set after assembly or the mentioned repair with the help of a tool provided with a scale.
• the basic angle a is set to 32°, whereupon the conical coupling 5 is tightened.
• the releasing and tightening are carried out by means of screws, which are not shown in the figures, as they are not important for the substance of the invention and such connecting can be designed by any average designer.
• the unwanted independent movement between the internal and the external eccenters are prevented by tightening of the conical coupling 5 and the mutual positions becomes controllable only by means of shift of the spiral rod 17, and this only within the defined scope of angles given by the kinematics.
• the degree of freedom from the motor 29 remains unaltered.
• the spiral rod ⁇ 7 has two purposes. On the one hand it transfers rotational movement from the motor to the second eccentric weight for formation of vibrations during movement of the roller, and on the other hand it allows movement of the first eccentric weight with regard to the other one for continuous setting of the vibration amplitude.
• the first or the second spiral toothing is right-handed, or left-handed. Important is only that always one hast to be left-handed and the other one right-handed.
• design of the subsequent transmissions has to be adapted to it. However, this can be carried out by any average designer, and therefore, it is not subject of the invention.
• the permitted size of vibrations can be determined both empirically, e.g. according to the surface type and mutual position of both weights, and by measuring, when the roller is provided by a sensor of real vibrations. Moreover, in machines with two vibration rollers arranged in tandem, it is possible to modify vibrations of both rollers to each other , to prevent addition of both vibrations.
• the other example of an embodiment of the vibration system according to the present invention is the vibration roller with divided runner.
• Fig. 5 and Fig. 6 show vibration device according to the present invention for the divided runner, which allows different rotational speed for the left and the right halves of the roller, what is suitable e.g. for rolling of the asphalt surface in curves etc.
• Design of a roller with a runner divided into two halves is commonly known. Therefore, it will not be discussed here as such any further.
• the vibrations are adjusted together of both the left and the right half of the runner, because difference in their speeds has not any influence on the size of vibrations.
• the two hydraulic motors for driving both halves of the runner are arranged at the sides of the roller body.
• the vibration device is arranged in one of the halves and it is similar to that in Fig. 1, whereby it is common for both halves of the runner.
• Fig. 5 shows a vibration roller comprising a vibration mechanism with circular vibration according to the present invention, which mechanism is provided with a divided runner 30.
• a hydraulic motor 29 In the axis of the vibration roller a hydraulic motor 29, a vibration mechanism 9 and a linear hydraulic motor 27 are arranged.
• the vibration mechanism 9 is rotationally supported on bearings 13 within the runner 30.
• the vibration mechanism 9 comprises especially a first eccentric weight 10 ⁇ in which weight J_0 the first sleeve 7 is firmly places with the respective internal sliding spiral toothing , and the second eccentric weight IT , in which the sleeve 8 with the respective internal sliding spiral toothings firmly supported . .
• the spiral toothing of the second sleeve 8 has opposite direction of the spiral than what is that of the spiral toothing of the first sleeve 7.
• the spiral rod 17 is appropriately provided with spiral toothings of both directions of rotation for cooperation with the respective spiral toothings of sleeves 7 and 8.
• the second eccentric weight ⁇ . is slidingly supported in bearings 3J, with regard to the first eccentric weight 10.
• the basic adjustment of the angle a is carried out, because of the absence of the conical coupling, which is not present here mainly because of space reasons, so that the first spiral toothing F5 and the second spiral toothing 16 are provided with different numbers of teeth, what allows to set up the position in steps given by the difference in the number of teeth in the first and the second spiral toothing. If both toothings have the same number of teeth, it is not possible to use the shift properly, as then the adjustment is given only by the angle corresponding to the difference of one tooth, what causes unacceptable roughness in the adjusting. However, in the embodiment with different number of teeth it is possible to use the resulting number of combinations, which number is given by a multiple of the number of teeth of the first and the second spiral toothings.
• a combination of 16 and 17 teeth is used, a consequence of which there are 272 possible positions within 360°. Therefore, if the first spiral gearing 15 with sixteen teeth is offset to the adjacent grooves of the sleeve 7 by one tooth, the spiral rod turns by 22.4°, but if the second spiral gearing 16 with seventeen teeth is also offset into the adjacent groves in its sleeve toothing 8, i.e. by one tooth, in the opposite direction, the spiral rod 17 turns back only by 21.1 °. The resulting turning of the spiral rod 17 is so only 1.3°, what allows the required accuracy in the adjustment.
• the vibration amplitude is changed continuously by changing the turning of the first eccentric weight 10 against the second eccentric weight ⁇ , what is carried out by axial shifting of the spiral rod 17, provided in this embodiment by the first spiral toothing 15, in this embodiment left-handed, and by the other spiral toothing 16, in this embodiment right-handed.
• the right-handed second spiral toothing 16 of the spiral rod 17 meshes with the right-handed spiral in the sleeve 8.
• the left-handed first spiral toothing 15 of the spiral rod ⁇ 7 meshes with the left-handed spiral of the sleeve 7.
• the first eccentric weight 10 is swivelled against the second eccentric weight 1 1 by the required angle over the spiral 15 meshing with the sleeve 7, which is firmly connected with the first eccentric weight 10, and over the spiral 16 meshing with the sleeve 8, which is firmly connected with the second eccentric weight IT .
• the first eccentric weight can comprise both the external and the internal eccentric weight and in the same way under the meaning of the term
• the term it is to understand that it is in reality the complementary eccentric weight to the first one, it is that if the first eccentric weight is the external one, the second is the internal one, and vice versa and that, therefore, it is not possible to limit the terms the first and the second eccentric weight exactly to the arrangement according to the figures, but that the reference numbers indicating these terms are only illustrative and serve for better understanding of the substance of the invention.
• Both examples of the invention according to Figures 1 and 5 preferably have the same method of control.
• the required position of the first eccentric weight 10 with regard to the second eccentric weight ⁇ is adjusted by the actuator 24, or automatically by the controlling unit 19.
• Information from the actuator 24 or from the control unit 19 enter the controller 23 ⁇ where they are compared with the information on real position of the first eccentric weight 10 with regard to the second eccentric weight ⁇ , determined by the sensor 28.
• the controller 23 evaluates the actual state and adjusts the distributor 22 in the desired position.
• the oil flowing through the proportional distributor 22 and hydraulic hoses 25 moves the piston 27 of the linear hydraulic motor 26 into the required position determined by the actuator 24, or automatically by the controlling unit 19.
• the invention can be used especially in the earth compacting machines for compacting of the subsoil, for example of the asphalt macadam, with at least one roller equipped with a vibration system for intensifying of the compacting. It is especially preferable also for the machines with two rollers equipped with vibration system.

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• Engineering & Computer Science (AREA)
• Architecture (AREA)
• Civil Engineering (AREA)
• Structural Engineering (AREA)
• Mechanical Engineering (AREA)
• Apparatuses For Generation Of Mechanical Vibrations (AREA)
• Road Paving Machines (AREA)
• Investigation Of Foundation Soil And Reinforcement Of Foundation Soil By Compacting Or Drainage (AREA)

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• 2012
  • 2012-03-12 CZ CZ20120173A patent/CZ2012173A3/cs not_active IP Right Cessation
• 2013
  • 2013-03-11 ES ES13718079T patent/ES2714315T3/es active Active
  • 2013-03-11 EP EP13718079.0A patent/EP2825703B1/en active Active
  • 2013-03-11 WO PCT/CZ2013/000034 patent/WO2013135215A1/en active Application Filing

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