EP3384096A1 - Arrangement for providing a pulsing compressive force - Google Patents
Arrangement for providing a pulsing compressive forceInfo
- Publication number
- EP3384096A1 EP3384096A1 EP15812936.1A EP15812936A EP3384096A1 EP 3384096 A1 EP3384096 A1 EP 3384096A1 EP 15812936 A EP15812936 A EP 15812936A EP 3384096 A1 EP3384096 A1 EP 3384096A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- mass
- spring
- damper system
- arrangement
- arrangement according
- 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.)
- Granted
Links
- 230000008878 coupling Effects 0.000 claims abstract description 40
- 238000010168 coupling process Methods 0.000 claims abstract description 40
- 238000005859 coupling reaction Methods 0.000 claims abstract description 40
- 230000003068 static effect Effects 0.000 claims abstract description 34
- 230000005484 gravity Effects 0.000 claims abstract description 31
- 230000010355 oscillation Effects 0.000 claims abstract description 15
- 230000003534 oscillatory effect Effects 0.000 claims description 49
- 238000005056 compaction Methods 0.000 claims description 22
- 239000002689 soil Substances 0.000 claims description 20
- 238000000034 method Methods 0.000 claims description 10
- 238000013016 damping Methods 0.000 claims description 9
- 239000010426 asphalt Substances 0.000 claims description 7
- 238000005553 drilling Methods 0.000 claims description 2
- 239000007787 solid Substances 0.000 claims 1
- 229920002635 polyurethane Polymers 0.000 description 11
- 239000004814 polyurethane Substances 0.000 description 11
- 239000000758 substrate Substances 0.000 description 5
- 239000006096 absorbing agent Substances 0.000 description 3
- 230000005284 excitation Effects 0.000 description 3
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 238000013467 fragmentation Methods 0.000 description 2
- 238000006062 fragmentation reaction Methods 0.000 description 2
- 229910052500 inorganic mineral Inorganic materials 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 239000011707 mineral Substances 0.000 description 2
- 101100388509 Caenorhabditis elegans che-3 gene Proteins 0.000 description 1
- 235000010678 Paulownia tomentosa Nutrition 0.000 description 1
- 240000002834 Paulownia tomentosa Species 0.000 description 1
- 239000011449 brick Substances 0.000 description 1
- 150000001875 compounds Chemical class 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 229920001971 elastomer Polymers 0.000 description 1
- 230000009191 jumping Effects 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
Classifications
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
- E02D3/00—Improving or preserving soil or rock, e.g. preserving permafrost soil
- E02D3/02—Improving by compacting
- E02D3/046—Improving by compacting by tamping or vibrating, e.g. with auxiliary watering of the soil
- E02D3/074—Vibrating apparatus operating with systems involving rotary unbalanced masses
Definitions
- the invention relates to an arrangement for providing a pulsating compressive force, a soil compacting device comprising such an arrangement, the use of the soil compaction device for compaction of asphalt and a method for operating such an arrangement or soil compaction device according to the preambles of the independent claims.
- ground compaction forces can be achieved with simple compaction equipment in on-load operation (permanent ground contact), which correspond to 2 times the machine weight for a short time. If a temporary lifting of the ground contact area from the ground is permitted, it is even possible to achieve soil compaction forces which correspond to 2.5 times the machine weight for a short time.
- the plate or the roller body is connected via a spring-damper system with an absorber mass arranged above it, which is also excited via the spring-damper system to vibrate. Oscillates the absorber mass in phase with the same frequency (1: 1 resonance) or Half the frequency (2: 1 resonance) of the plate or the roller body, so can be achieved with this machine concept soil compaction forces, which correspond to more than three times the weight of the machine, when the Ab ⁇ lift the ground contact surface from the ground is allowed.
- soil compacting devices are known, for example, from WO 2011 / - 127611 A2.
- a first aspect of the invention relates to an arrangement ⁇ to provide a pulsating pressure force.
- the arrangement comprises a first Mas ⁇ se, which provides a contact surface for transmitting the pulsating compressive force on a corporeality, for example, to a bottom surface to be compacted.
- the arrangement comprises a second mass, which is coupled to each other via a first spring-damper system with the first mass to a first oscillatory system.
- the arrangement comprises an unbalance exciter, by means of which this oscillatory system can be excited to oscillate, preferably to resonant oscillations.
- the second mass exerts a static force in a first direction on the first mass via the first spring-damper system.
- the coupling of the first mass and the second mass via the first spring-damper system is realized such that no forces are transmitted from the first mass in the first direction to the second mass via the first spring-damper system during normal operation and can no forces from the second mass in a second direction which is directed opposite to the ers ⁇ th direction, to the first mass may be transferred.
- the arrangement is structurally designed such that this so-called “unilateral coupling" of the two masses on the first spring-damper system during normal operation be ⁇ preferably periodically (ie repeated at regular intervals) by a swinging motion of the second mass in the second direction can temporarily be canceled and the second mass then perform a part of their swing path in the decoupled state p before after doing a reversal of direction of the swinging motion of the second mass, the coupling of the two masses on the first spring-damper system is restored in particular abruptly
- the bearing or guiding of the second mass is thus configured in such a way that, during normal operation, it can execute a movement path in which the temporary decoupling described above is possible.
- the mutatis mutandis reverse coupling situation is provided, i. the first mass is temporarily decoupled from the first spring-damper system.
- one or the other variant may be more advantageous.
- the second mass exerts a static pressure force on the first mass in the static state of the first oscillatory system via the first spring-damper system.
- the first mass and the second mass are coupled to one another in such a way via the first spring-damper system that only pressure forces between the two masses can be transmitted via the first spring-damper system.
- Spring damper system exerts a static pulling force on the first mass.
- the first and the second mass are coupled to one another in such a way via the first spring / damper system that exclusively tensile forces can be transmitted between the two masses via the first spring / damper system.
- the constructive configuration of the arrangement one or the other variant can also be more advantageous here.
- the static force exerted on the first mass by the second mass via the first spring-damper system in the static state of the first oscillatable system extends essentially in the direction of gravity.
- Such arrangements according to the invention are particularly suitable for soil compacting devices and piling devices.
- the static force exerted on the first mass by the second mass via the first spring / damper system in the static state of the first oscillatable system is entirely or at least partially transmitted through the first mass Weight of the second mass is generated.
- the static force exerted on the first mass by the second mass via the first spring-damper system in the static state of the first oscillatory system is generated entirely or at least partially by a force acting on the second mass.
- this embodiment is advantageous to necessary.
- the force acting on the second mass acts on the mass via one or more spring elements.
- the vibration behavior of the second mass can be adjusted in a targeted manner.
- the one or more spring elements are ver ⁇ connected with the first mass, so that in the static state of the first oscillatory system via this or these Federele- elements transmit a force to the first mass which acts in the second direction.
- the first mass and the second mass via a further spring-damper system are coupled together.
- the spring constant and / or the damping of this further spring-damper system is smaller than the spring constant and / or the damping of the first spring-damper system.
- Embodiment of the arrangement further preferred that the first mass and the second mass are coupled to each other via the further spring-damper system, that between the other spring-damper system and the two masses forces in the first direction and in the second direction are transferable.
- the further spring-damper system couples in this variant, the two masses so both sides, i. such that both tensile and compressive forces can be transmitted between the masses.
- the first mass and the second mass are coupled to each other via the further spring-damper system in such a way that no forces from the second mass in the first direction to the first via the further spring-damper system Mass are transferable and no forces from the first mass in the second direction to the second mass are transferable.
- the further spring / damper system thus couples the two masses to one another in such a way that only either tensile or Compressive forces between the masses can be transmitted.
- the arrangement is designed such that this so-called “unilateral coupling" of the two masses on the further spring-damper system during normal operation preferably periodically repealed by a swinging movement of the second mass in the first direction and the second mass then can perform a part of its oscillating path in the decoupled state before the coupling of the two compounds is prepared by the further spring-Dämp ⁇ fer system in particular abruptly after a while fully led Rich ⁇ tung reversing the oscillating movement of the second mass.
- a third mass which is coupled to the first mass via a second spring-damper system to a second oscillatory system and / or which with the second mass via a third spring-damper system is coupled to a third oscillatory system.
- this third mass can serve, for example, as a "Ruhepol”, which makes virtually no oscillatory movement and for the arrangement of drive motors, controls and controls and, in the case of vertical orientation of the first direction, additionally forms a load in this direction, or can also serve as a "damping mass", which in particular in phase with the first mass oscillates, in particular with the oscillation frequency of the first mass or with half or one third of the oscillation frequency of the first mass, and thereby additionally contributes a part of the pulsating compressive force in the first direction.
- the third mass and the first mass via a second spring-damper system are mitein ⁇ other coupled, that between the second spring-damper system and these two masses both forces in the first Direction as well as in the second direction are transferable.
- the second spring-damper system thus couples these two masses to one another on both sides, ie in such a way that both tensile and compressive forces can be transmitted between these masses.
- the third mass and the second mass are coupled to one another via a third spring-damper system in the manner described above.
- the coupling of the third mass and the second mass is such that both forces in the first direction and in the second direction can be transmitted between the third spring-damper system and these two masses, these two So masses are coupled on both sides, so that both tensile and compressive forces can be transmitted between these masses.
- the third mass and the second mass are coupled together via the third spring-damper system in such a way that no forces can be transmitted from the second mass in the first direction to the third mass via the third spring-damper system and no forces from the third mass in the second direction to the second mass are transferable.
- the third spring-damper system coupled in this variant, these two masses so one-sided, such that only either tensile or compressive forces can be transmitted between these masses.
- the arrangement is configured such that this so-called “unilateral coupling" of the two masses via the third spring-damper system in Bestiramungsgefflessen operation can be temporarily suspended temporarily by a swinging motion of the second mass in the first direction and the second mass Then, in the decoupled state can perform a part of their swing path, before after doing a reversal of direction while the Schwingbewe ⁇ tion of the second mass, the coupling of the two masses on the third spring-damper system in particular shock ⁇ is restored.
- the oscillatory systems of the arrangement according to the invention are set or adjustable in such a way that the second mass is in phase with the first mass when the first oscillatory system (first mass, first spring-damper system, second mass) resonates in the intended operation oscillates, in particular with the oscillation frequency of the first mass or with half or one third of the oscillation frequency of the first mass.
- first oscillatory system first mass, first spring-damper system, second mass
- the assembly has a third mass coupled to the first mass via a second spring-damper system to a second oscillatable system and / or to the second mass via a third spring Damper system is coupled to a third oscillatory system provided that the oscillatory systems of the arrangement are set or adjustable such that in the normal operation of the arrangement in a preferably resonantly oscillating first oscillatory system (first mass, first spring damper system).
- System, second mass the third mass in the Essentially no oscillatory motion performs.
- the third mass for example, serve as a "Ruhepol" and is suitable for the arrangement of drive motors, controls and controls it.
- the unbalance exciter of the arrangement according to the invention which is preferably designed as a directional oscillator or as a circular oscillator, forms part of the first mass or part of the second mass with Vor ⁇ part and stimulates this mass in normal operation to oscillate.
- particularly large pulsating pressure forces can be generated.
- the claimed second mass is formed by a plurality of sub-masses, preferably by exactly two sub-masses, which are advantageously the same weight. These sub-masses are coupled in each case via its own claim according to the first spring-damper system with the first mass to its own claim according to the first oscillatory system.
- the contact surface provided by the first mass for transmitting the pulsating compressive force to a corporeality is preferably the outer surface of the bandage of a roller, the underside of the bottom plate of a vibrating plate, the working surface of a chisel or boring tool or the contact surface of the vibrating beam of a paver.
- the second mass is formed by one or a plurality of annular weights or includes such which are arranged within the bandage and can perform therein a swinging movement in a direction transverse to the longitudinal axis of the bandage.
- a second aspect of the invention relates to a soil compaction apparatus comprising an assembly according to the first aspect of the invention, namely be ⁇ vorzugtluate a vibrating plate or roller, preferably vibration excited by one or two drums.
- a third aspect of the invention relates to
- a fourth aspect of the invention relates to
- the contact surface of the first mass for example, the underside of the bottom plate of a device equipped with the inventive arrangement vibration plate or the drill tip of an inventive arrangement equipped rotary hammer, brought into contact with a physicality, for example, with a bottom surface to be compacted or one with a bore to be provided building wall.
- the first oscillatory system When in contact with the physical contact surface, the first oscillatory system is excited with the unbalance exciter to vibrate such that the Kopp ⁇ ment of the two masses on the first spring-damper system by a swinging motion of the second mass in the second direction , Preferably, at regular intervals (periodically), temporarily canceled, the second mass then performs in the decoupled state, a part of their swing path, and then the coupling of the two masses on the first spring-damper system after a direction reversal of the oscillatory motion of the second mass is in particular abruptly restored.
- the inventive method is particularly large pulsating pressure forces to be processed physicality can initiate, and in the case of operation of soil compacting devices in Auflast memori (permanent contact with the ground) soil compaction forces it ⁇ locations, which are briefly significantly greater than 2-fold of the machine weight.
- the contact surface of the first mass is kept in contact with the physicality during exposure to the corporeality.
- This variant of the method is of particular importance in the compaction of asphalt, since jumping the contact surface of the compacting device would lead to fragmentation of the mineral material in the asphalt surface, which must be avoided at all costs.
- the oscillatory systems of the arrangement are excited to oscillate in such a way that the second mass oscillates in phase with the first mass, preferably with the oscillation frequency of the first mass or with half or with one third of the oscillation frequency of the first mass.
- an inventive An ⁇ order is used, which has a third mass, and it will be the vibratable systems the arrangement derar- excited tig to vibrations that the third mass essentially performs no oscillating motion.
- Figures la and 1b the vibration control models of two variants of a first inventive arrangement
- FIGS. 3a and 3b show the vibration-technical models of two variants of a third arrangement according to the invention
- FIGS. 4a and 4b show the vibration-technical models of two variants of a fourth arrangement according to the invention.
- FIGS. 5a and 5b show the vibration-technical models of two variants of a fifth arrangement according to the invention.
- 5c shows the vibration-technical model of a sub-variant of the variant shown in FIG. 5a;
- FIGS. 7a and 7b show the vibration-technical models of two variants of a seventh arrangement according to the invention.
- FIG. 10 is a side view of erfindungsgemäs ⁇ sen tandem roller for asphalt compaction
- FIG. 11 shows a section through the front bandage of the tandem roller from FIG. 10 along the line A-A;
- FIG. 12 is an illustration like FIG. 11 of an embodiment of the bandage
- FIG. and Fig. 13 is a representation like Fig. 11 of another embodiment of the bandage.
- FIGS. 1 a and 1 b show the vibration-mechanical models of two variants of a first arrangement according to the invention for providing a pulsating pressure force, which is part of a vibration-excited roller for compaction of the soil.
- this arrangement comprises a first mass 1, which provides a contact surface 2 in the form of the outer surface of the bandage of the roller for transmitting the pulsating compressive force to the Bodenflä ⁇ che 3 to be compacted. Furthermore, the arrangement comprises a second mass 4, which is coupled via a spring-damper system 5, 6 (according to the claims first spring-damper system) with the first mass 1 to a vibratory system 1, 4, 5, 6 (according harnessgemässes first oscillatory system).
- the arrangement comprises an unbalance exciter 7, by means of which this oscillatory system 1, 4, 5, 6 can be excited to vibrate.
- this oscillatory system 1, 4, 5, 6 can be excited to vibrate.
- the second mass 4 exerts due to their weight force on the spring-damper system 5, 6 a static force in the direction Sl (demanding first direction) on the first mass which in the present case is identical to the gravitational direction.
- the first mass 1 and the second mass 4 are coupled to one another via the spring / damper system 5, 6 in such a way that no forces from the first mass 1 in the direction S1 to the first mass 1 in the direction S1 are produced by this system 5, 6 second mass 4 can be transmitted and no forces from the second mass 4 in a direction S2 (claim second direction), which is opposite to the direction Sl, can be transmitted to the first mass 1.
- the second mass 4 in the static state of the system 1, 4, 5, 6 via the spring damper system 5, 6 exerts a static compressive force in the direction of gravity on the first mass 1 and the coupling is such that over the spring-damper system 5, 6 exclusively compressive forces between the two masses 1, 4 can be transmitted.
- the arrangement shown here model is further designed such that the coupling of the two masses 1, 4 via the spring-damper system 5, 6 in normal operation periodically by a
- Swinging motion of the second mass 4 in the direction S2, i. contrary to the direction of gravity, can be temporarily suspended, the second mass then perform a part of their swing path in the decoupled state, and the coupling via the spring-damper system 5, 6 then after a reversal of direction of the swinging motion of the second mass 4 is restored.
- the temporary cancellation of the coupling of the two masses 1, 4 via the spring-damper system 5, 6 takes place by a temporary decoupling of the second mass 4 of the spring-damper system 5, 6. This coupling situation is shown in the figures indicated by the distance between the spring-damper system 5, 6 and the second mass 4.
- the variants according to FIGS. 1 a and 1 b differ only in that in the former variant the unbalance exciter 7 is part of the first mass 1 and excites it to vibrate during normal operation, whereas in the last-mentioned variant it is part of the second mass 4 it is within the intended use Operation to vibrate. This is also the only difference between the variants of the various embodiments of the arrangement according to the invention, each of which is labeled "a" and "b" below.
- FIGS. 2 a and 2 b show the vibration-technical models of two variants of a second invention.
- the arrangement according to the invention for providing a pulsating compressive force which differs from the embodiment shown in FIGS. 1a and 1b only in that the first mass 1 and the second mass 4 are additionally coupled to one another via a further spring-damper system 8, 9, whose spring constant and damping is smaller than the spring constant and damping of the first spring-damper system 5, 6.
- the first mass 1 and the second mass 4 are such over this further
- FIGS. 3 a and 3 b show the vibration-mechanical models of two variants of a third arrangement according to the invention for providing a pulsating compressive force, which differs from the embodiment shown in FIGS. 2 a and 2 b only in that here the first mass 1 and the second Mass 4 such on the other spring-damper system 8, 9 are coupled together that on this spring damper system 8, 9 in normal operation no forces from the second mass 4 in the direction Sl, ie in the direction of gravity, can be transmitted to the first mass 1 and from the first mass 1 no forces in the direction S2, i. against the direction of gravity, can be transferred to the second mass 4.
- the arrangement is also be madestal ⁇ tet such that the coupling of the two masses 1, 4 via the further spring-damper system 8, 9 in normal operation periodically by a swinging motion of the second mass 4 in the direction Sl, ie in the direction of gravity, can be temporarily suspended, the second mass then perform a decoupled state, a part of their swing path, and the coupling of the two masses 1, 4 via this further spring-damper system 8, 9 then to a direction reversal of the oscillatory movement of the second mass 4, ie in the subsequent upward movement of the second mass 4, is restored.
- Embodiments according to the figures la, lb, 2a, 2b, 3a and 3b basically once by having a third mass 10.
- FIGS. 4a and 4b show the basic construction of the embodiment shown in FIGS. 1a and 1b, the third mass 10 having the second mass 4 being connected via a spring-damper system 8a, 9a (third spring-damper system according to the invention). is coupled to an additional schwingfähi ⁇ gen system 4, 10, 8a, 9a (according to the claims third vibratable system).
- the coupling is designed in such a way that between this spring damper system 8a, 9a and the two masses 10, 4 forces in the two directions Sl, S2, ie both in the direction of gravity and against the direction of gravity, are transferable. It can this spring Dämp ⁇ fer system 8a, 9a tensile and compressive forces between the second mass 4 and the third mass 10 will carry both exceeded.
- the fifth arrangement according to the invention according to FIGS. 5a and 5b likewise has the basic structure of the embodiment illustrated in FIGS. 1a and 1b, in which case the third mass 10 with the first mass 1 via a spring-damper system 11, 12 (second spring according to the invention Damper system) is coupled to an additional oscillatory system 1, 10, 11, 12 (according to claim second oscillatory system).
- the coupling is designed such that between this spring-damper system 11, 12 and the two masses 1, 10 forces in both directions Sl, S2, ie in gravity direction and against the direction of gravity, are transferable. It can therefore be transmitted via this spring-damper system 11, 12 both tensile and compressive forces between the first mass 1 and the third mass 10.
- Fig. 5c shows the vibration model of a technical subvariant to that shown in Fig. 5a Anord ⁇ voltage variation. As can be seen, this only differs from the arrangement according to FIG. 5a in that the second mass 4 is divided here into two partial masses 4a, 4b, each of which has its own spring-damper system 5, 6 with the first mass 1 to a vibratory system 1, 4a, 5, 6 and 1, 4b, 5, 6 ge ⁇ coupled.
- the sixth arrangement according to the invention according to FIGS. 6a and 6b has the basic structure of the embodiment shown in FIGS. 2a and 2b, the third mass 10 having the first mass 1 being connected via a spring / damper system 11, 12 (according to the claimed second embodiment). Damper system) is coupled to an additional oscillatory system 1, 10, 11, 12 (according to the claim second oscillatory system). The coupling is designed such that between this spring-damper system 11, 12 and the two masses 1, 10 forces in both directions Sl, S2, i. as well in
- FIGS. 7a and 7b differ from the embodiment illustrated in FIGS. 6a and 6b only in that here the third mass 10 additionally, as in the embodiment shown in FIGS. 4a and 4b, is connected to the second mass 4 via a spring.
- Damper system 8a, 9a third damper spring system according to the invention. tem) to an additional oscillatory system 4, 10, 8a, 9a (claim third third oscillatory system) is coupled.
- the coupling is designed such that between this spring-damper system 8a, 9a and the two masses 10, 4 forces in both directions Sl, S2, ie both in the direction of gravity and against the
- Direction of gravity can be transmitted to the third mass 10 and from the third mass 10 no forces in the direction S2, ie in the direction opposite to the gravitational force direction, can be transmitted to the second mass 4.
- the arrangement is further designed such that this coupling of the two masses 4, 10 via the Fe ⁇ damper system 8a, 9a in normal operation periodically by a swinging motion of the second mass 4 in the direction Sl, ie in the direction of gravity, past ⁇ can be lifted, the second mass then perform a part of their swing path in the decoupled state, and the coupling of the two masses 4, 10 via the spring-damper system 8a, 9a then after a reversal of direction of the oscillatory motion of the second mass 4, ie in the subsequent movement in the direction S2 against the direction of gravity, is restored.
- the fundamental construction corresponds to the embodiment of the arrangement shown in FIG. 4b.
- the arrangement shown here is part of a hammer drill.
- the contact surface 2, which provides the first mass 1 here consists of the tip 2 of a drill 14, with which a hole in a building wall 13, for example made of brick, is drilled.
- the two directions S1 and S2 run horizontally here, which is why the weight forces of the masses 4, 10 do not produce any coupling or restoring forces and in the direction of S1, that is, acting from the outside on the third mass 10
- FIG. 10 shows a side view of a tandem roller according to the invention with an operating weight of approximately 4.5 t.
- the roller has two vibration-excited belts ⁇ dagen 1 with smooth outer surfaces 2, which each have an outer diameter of 85 cm.
- each bandage 1 forms together with an unbalance exciter 7 arranged in its center, with two each in the Be ⁇ Rich one of the ends of the bandage in the bandage 1 vertically freely movable arranged additional mass rings 4a, 4b and with the coupled to the drum 1 roll chassis 10 an inventive arrangement for providing a pulsating compressive force according to the in Fig. 5c dargestell ⁇ th vibration control model.
- the bandage 1 is in each case in the area surrounding the additional mass rings 4a, 4b, lined on its inside with a 1 cm thick mat of polyurethane 5, 6 with a density of about 1.25 g / cm3
- the mats 5, 6 each form a a first spring-damper system according to the present invention for the swingable coupling of the respective additional mass ring 4a or 4b to the bandage 1.
- the additional mass rings 4a, 4b rest on these mats 5, 6 with their weight force in the direction of gravity S1 and are thus above the polyurethane mats 5 , 6 unilaterally coupled to the bandage 1.
- the bandage 1 with unbalance exciter 7 (demanding first mass) has a weight of about 750 kg.
- the additional mass rings 4a, 4b (claim-compliant second mass) each have a basis weight of 100 kg and can be loaded with attachable additional weights in 7.5 kg steps up to a weight of 160 kg each.
- the unbalance exciters 7 comprises a single Un ⁇ balancing shaft 21 (circular motion) at a fixed unbalance of about 0.05 kgm, which is mounted in two vertical walls 15a, 15b in the drum 1 and can be rotatably driven via a Hydrau ⁇ likmotor sixteenth
- the roll chassis 10 (claim third mass) is supported with a weight of about 1100 kg on two arms 17a, 17b, which laterally enter the ends of the bandage 1, on the bandage 1, which rotatable relative to the chassis 10 about a horizontal axis is stored around.
- the roll chassis 10 is coupled to the drum 1 via rubber vibration dampers 11, 12, which form a second spring-damper system in accordance with the requirements, such that the roller chassis 10 is decoupled from the drum 1 essentially in terms of vibration.
- the storage via a roller bearing 18, which is rigidly connected to the bandage 1, and on the right side via a bandage drive motor 19 formed by a bearing unit 20, which is rigid with the right arm 17a of the roll chassis 10 is connected.
- the imbalance shaft 21 is set in rotation with the hydraulic motor 16 and then generates pulsating exciter forces with a desired excitation frequency (typically in the range between 40 Hz and 100 Hz).
- a desired excitation frequency typically in the range between 40 Hz and 100 Hz.
- the rotation frequency of the imbalance shaft 21 (excitation frequency) and a possible increase in the additional mass rings 4a, 4b with additional weights selected such that the additional mass rings 4a, 4b periodically in a direction S2 against the direction of gravity Sl temporarily stand out from the polyurethane mats 5, 6, in this decoupled ⁇ th state perform a part of their swinging path in this direction S2, and then, after a whosum ⁇ turn again move in the direction of gravity Sl and again on the polyurethane mats 5, 6 impinge.
- the outer surface 2 of the bandage 1 remains permanently in contact with the substrate to be compacted.
- the rotational frequency and any weighting with additional weights can vary greatly in order to produce this operating state.
- FIG. 12 shows a vertical section as in FIG. 11 through an embodiment variant which differs from the embodiment shown in FIG. 11 only in that two additional mass-mass rings 4a, 4b are arranged in the center of the bandage 1 instead of the two additional mass-rings 4a arranged in the end regions of the bandage 1 a singleificatmas ⁇ senring 4 (claim second mass) is arranged, which is vertically movable freely in the bandage 1 and is penetrated by the Unwuchtv / elle 21 of the unbalance exciter 7.
- the vibrational model of this embodiment is shown in Fig. 5a.
- the additional mass ring 4 is located with his
- the imbalance shaft 21 is set in rotation by the hydraulic motor 16 and the bandage 1 and the additional mass ring 4 are thus vibrated such that the additional mass ring 4 periodically lifts off the polyurethane mat 5, 6 in the direction S2 against the direction of gravity S1 , Performs in this decoupled state a part of its oscillation travel in this direction S2, and then, after reversing direction again moves in the direction of gravity ⁇ Sl and again impinges on the polyurethane mat 5, 6.
- the outer surface 2 of the bandage 1 remains permanently in contact with the substrate to be compacted.
- the rotational ⁇ frequency of the imbalance shaft can vary greatly to produce this operating state.
- FIG. 13 shows a vertical section as in FIG. 11 through a further embodiment, which differs from the embodiment shown in FIG. 12 only in that the additional mass ring 4 has end end walls 22a, 22b and the unbalance element 21 is not in the two
- the rotary coupling of the imbalance shaft 21 to the hydraulic motor 16 is realized via a propeller shaft 23, such that the free vertical mobility of the additional mass ring 4th is not hindered by this coupling.
- the vibrational model of this embodiment variant is in Fig. 5b shown. As can be seen, forms the imbalance shaft 21 here together with the additional mass ring 4, the claimed second mass.
- the imbalance shaft 21 is offset by the hydraulic motor 16 in rotation and the additional mass ring 4 and the bandage 1 are thereby vibrated such that the additional ⁇ mass ring 4 with the imbalance shaft 21 mounted therein periodically in the direction S2 against the direction of gravity Sl temporarily lifted off of the polyurethane mat 5, 6, in this decoupled state performs a part of its oscillation travel in this direction S2, and then, after a reversal of direction, moves again in the direction of gravity Sl and impinges again on the polyurethane mat 5, 6.
- the outer surface 2 of the bandage 1 remains permanently in contact with the substrate to be compacted.
- the rotational frequency of the imbalance shaft 21 can vary greatly in order to produce this operating state.
Abstract
Description
Claims
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/CH2015/000178 WO2017091912A1 (en) | 2015-12-03 | 2015-12-03 | Arrangement for providing a pulsing compressive force |
Publications (2)
Publication Number | Publication Date |
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EP3384096A1 true EP3384096A1 (en) | 2018-10-10 |
EP3384096B1 EP3384096B1 (en) | 2022-08-03 |
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP15812936.1A Active EP3384096B1 (en) | 2015-12-03 | 2015-12-03 | Arrangement for providing a pulsing compressive force |
Country Status (6)
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US (1) | US10428482B2 (en) |
EP (1) | EP3384096B1 (en) |
JP (1) | JP2018536106A (en) |
AU (1) | AU2015416104A1 (en) |
CA (1) | CA3006611A1 (en) |
WO (1) | WO2017091912A1 (en) |
Families Citing this family (1)
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DE102019132917A1 (en) * | 2019-12-04 | 2021-06-10 | Hamm Ag | Tillage roller |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6742960B2 (en) * | 2002-07-09 | 2004-06-01 | Caterpillar Inc. | Vibratory compactor and method of using same |
DE202004014585U1 (en) | 2004-09-16 | 2006-01-26 | Weber Maschinentechnik Gmbh | Vibration exciter for e.g. compaction roller, has imbalance mass arranged on pivoted imbalance-shaft and force transmission unit moving imbalance mass, such that angular speed of imbalance mass is varied during each revolution |
DE202009004302U1 (en) | 2008-04-01 | 2009-11-12 | Wacker Neuson Se | Vibrating plate with intermediate mass |
BR112012026543A2 (en) | 2010-04-16 | 2016-07-12 | Ammann Schweiz Ag | arrangement for preparing a pulsating compressive force |
US8608403B2 (en) * | 2012-03-28 | 2013-12-17 | Caterpillar Paving Products Inc. | Magnetic vibratory compactor |
-
2015
- 2015-12-03 WO PCT/CH2015/000178 patent/WO2017091912A1/en active Application Filing
- 2015-12-03 CA CA3006611A patent/CA3006611A1/en not_active Abandoned
- 2015-12-03 JP JP2018548249A patent/JP2018536106A/en active Pending
- 2015-12-03 AU AU2015416104A patent/AU2015416104A1/en not_active Abandoned
- 2015-12-03 US US15/780,316 patent/US10428482B2/en active Active
- 2015-12-03 EP EP15812936.1A patent/EP3384096B1/en active Active
Also Published As
Publication number | Publication date |
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AU2015416104A1 (en) | 2018-06-14 |
CA3006611A1 (en) | 2017-06-08 |
WO2017091912A1 (en) | 2017-06-08 |
US20180355572A1 (en) | 2018-12-13 |
JP2018536106A (en) | 2018-12-06 |
EP3384096B1 (en) | 2022-08-03 |
US10428482B2 (en) | 2019-10-01 |
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