US20180258601A1 - Soil Compacting Device with Compensating Coupling - Google Patents
Soil Compacting Device with Compensating Coupling Download PDFInfo
- Publication number
- US20180258601A1 US20180258601A1 US15/915,501 US201815915501A US2018258601A1 US 20180258601 A1 US20180258601 A1 US 20180258601A1 US 201815915501 A US201815915501 A US 201815915501A US 2018258601 A1 US2018258601 A1 US 2018258601A1
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- Prior art keywords
- shaft
- drive
- exciter
- crank
- output shaft
- Prior art date
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- 230000008878 coupling Effects 0.000 title claims abstract description 69
- 238000010168 coupling process Methods 0.000 title claims abstract description 68
- 238000005859 coupling reaction Methods 0.000 title claims abstract description 68
- 239000002689 soil Substances 0.000 title claims abstract description 53
- 230000005540 biological transmission Effects 0.000 claims abstract description 41
- 229920001971 elastomer Polymers 0.000 claims description 16
- 239000000806 elastomer Substances 0.000 claims description 13
- 238000005056 compaction Methods 0.000 claims description 5
- 239000002184 metal Substances 0.000 description 11
- 239000000428 dust Substances 0.000 description 5
- 238000002485 combustion reaction Methods 0.000 description 4
- 230000002706 hydrostatic effect Effects 0.000 description 4
- 230000007774 longterm Effects 0.000 description 3
- 230000035515 penetration Effects 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 239000000872 buffer Substances 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000011109 contamination Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 239000002828 fuel tank Substances 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 239000003921 oil Substances 0.000 description 1
- 239000011435 rock Substances 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
Images
Classifications
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- 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
-
- 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
-
- 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
- B06B3/00—Methods or apparatus specially adapted for transmitting mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
-
- 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
- E01C19/30—Tamping or vibrating apparatus other than rollers ; Devices for ramming individual paving elements
- E01C19/34—Power-driven rammers or tampers, e.g. air-hammer impacted shoes for ramming stone-sett paving; Hand-actuated ramming or tamping machines, e.g. tampers with manually hoisted dropping weight
- E01C19/35—Hand-held or hand-guided tools
-
- 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
- E01C19/30—Tamping or vibrating apparatus other than rollers ; Devices for ramming individual paving elements
- E01C19/34—Power-driven rammers or tampers, e.g. air-hammer impacted shoes for ramming stone-sett paving; Hand-actuated ramming or tamping machines, e.g. tampers with manually hoisted dropping weight
- E01C19/38—Power-driven rammers or tampers, e.g. air-hammer impacted shoes for ramming stone-sett paving; Hand-actuated ramming or tamping machines, e.g. tampers with manually hoisted dropping weight with means specifically for generating vibrations, e.g. vibrating plate compactors, immersion vibrators
-
- 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
- E01C19/30—Tamping or vibrating apparatus other than rollers ; Devices for ramming individual paving elements
- E01C19/34—Power-driven rammers or tampers, e.g. air-hammer impacted shoes for ramming stone-sett paving; Hand-actuated ramming or tamping machines, e.g. tampers with manually hoisted dropping weight
- E01C19/40—Power-driven rammers or tampers, e.g. air-hammer impacted shoes for ramming stone-sett paving; Hand-actuated ramming or tamping machines, e.g. tampers with manually hoisted dropping weight adapted to impart a smooth finish to the paving, e.g. tamping or vibrating finishers
- E01C19/402—Power-driven rammers or tampers, e.g. air-hammer impacted shoes for ramming stone-sett paving; Hand-actuated ramming or tamping machines, e.g. tampers with manually hoisted dropping weight adapted to impart a smooth finish to the paving, e.g. tamping or vibrating finishers the tools being hand-guided
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/50—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members
- F16D3/60—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members comprising pushing or pulling links attached to both parts
Landscapes
- Engineering & Computer Science (AREA)
- Structural Engineering (AREA)
- Civil Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Life Sciences & Earth Sciences (AREA)
- Architecture (AREA)
- Environmental & Geological Engineering (AREA)
- Paleontology (AREA)
- Mining & Mineral Resources (AREA)
- General Life Sciences & Earth Sciences (AREA)
- Soil Sciences (AREA)
- Agronomy & Crop Science (AREA)
- Road Paving Machines (AREA)
Abstract
A soil compacting device has an upper mass having a drive and a lower mass having an imbalance exciter. On the lower mass, there is provided a bearer device connected fixedly thereto, which bearer device bears a transmission device having an input shaft and an output shaft. The drive has a drive shaft that is coupled to the input shaft. The imbalance exciter has an exciter shaft that is coupled to the output shaft. A compensating coupling is provided between the drive shaft of the drive and the input shaft of the transmission device. The compensating coupling is designed to compensate for an axial offset, a radial offset, and an angular offset between the drive shaft and the input shaft.
Description
- The present invention relates to a soil compacting device, such as a vibrating plate or vibratory plate compactor.
- Vibrating plates for soil compaction are known. They are standardly designed such that they have an upper mass, which bears a drive motor, and a lower mass, coupled to the upper mass so as to be movable relative thereto. On the lower mass, there is provided an imbalance exciter that is attached to a soil contact plate and that, during operation, introduces vibrations into this plate. The vibrations are transferred into the soil to be compacted via the soil contact plate.
- The imbalance exciter can standardly have one, two, or three imbalance shafts that are rotationally driven. When there is rotation of the imbalance shaft or shafts, due to the imbalance mass attached to the respective imbalance shaft (a plurality of imbalance masses may also be attached) the desired imbalance forces arise, which cause the vibrations.
- For the drive of the imbalance exciter, two systems have primarily proven successful, namely a hydrostatic drive and a V-belt drive.
- In the hydrostatic drive, hydraulic oil is pressurized via a gear pump seated on an internal combustion engine on the upper mass, which oil drives a gear motor seated on the lower mass and fastened to the imbalance exciter. The two gear units are connected to one another via hydraulic hoses. The compensation of the relative movements between the upper mass and the lower manse is enabled by the flexibility of the hydraulic hoses.
- An example of a vibrating plate generally known from the prior art having a V-belt drive is shown in
FIGS. 5A and 5B ; hereFIG. 5A shows a highly schematized side view andFIG. 5B shows a view from the rear. - In a V-belt drive, a first V-
belt pulley 51 is provided on aninternal combustion engine 52, which is always installed transversely, on anupper mass 53. A second V-belt pulley 54 is fastened on anexciter shaft 55, which is always installed transversely, on an imbalance exciter 56 of alower mass 57. A V-belt 58 that runs over bothpulleys upper mass 53 andlower mass 57. - The required V-belt tension in V-belt drives is frequently achieved through self-tensioning pulleys. Alternatively, a tension roller can also be provided that tensions the belt and is adjusted manually using a tool. In these tensioning systems, only the average required belt tension is applied. These systems are relatively sluggish and are capable only to a certain extent of compensating the rapid relative movements that occur during vibration operation between the upper mass and the lower mass, and the associated changes in axial spacing between the two shafts.
- Due to the permanent relative movement between the upper mass and the lower mass, the V-belt circulating between the two pulleys is exposed to significant load, for which it is usually not designed. The lifespans indicated by the manufacturers of commercially available V-belts can be achieved only if the pulleys have a defined, constant axial spacing and a high degree of parallel alignment to each other. In addition, a dust-free environment is presupposed, in particular one that is free of abrasive media.
- Because these requirements cannot be met during operation of a belt-driven vibrating plate, the service life of the V-belt is greatly limited. Failure of the belt results in a longer period of machine downtime, due to the work necessary to exchange the belt. In addition, the constantly changing axial distance enables an increased degree of slippage in the belt drive, which has a negative influence on the overall efficiency of the drive system.
- In comparison, the hydrostatic drive of the imbalance exciter has proven very successful in practice. However, it requires a significant additional constructive outlay, resulting in significantly greater weight and higher costs. For these reasons, the hydrostatic drive is mostly installed only in high-power vibrating plates. In smaller vibrating plates, in contrast, the inexpensive and economical V-belt drive is used.
- The object of the present invention is to indicate a soil compacting device in which the drive power can be transmitted from the drive present on the upper mass to the imbalance exciter on the lower mass in a constructively simple and thus low-cost manner.
- This object is achieved by providing a soil compacting device that has an upper mass that has a drive, a lower mass that is connected to the upper mass so as to be movable relative thereto, and a soil contact plate for soil compaction, an imbalance exciter provided on the lower mass and capable of being driven by the drive, and having a bearer device situated on the upper mass or on the lower mass and connected fixedly thereto. The bearer device has a transmission or gearbox device having an input shaft and an output shaft that are coupled by a torque-transmitting device for the transmission of a torque from the input shaft to the output shaft. The bearer device bears the input shaft and the output shaft so as to be capable of rotation. The drive has a drive shaft that is coupled to the input shaft. The imbalance exciter has an exciter shaft that is coupled to the output shaft. Between the drive shaft of the drive and the input shaft of the transmission device or, in an alternative specific embodiment, between the output shaft of the transmission device and the exciter shaft of the imbalance exciter, a compensating coupling is provided. The compensating coupling is designed to compensate an axial offset, a radial offset, and an angular offset between the drive shaft and the input shaft, or, in the alternative specific embodiment, between the output shaft and the exciter shaft.
- The soil compacting device can for example be a vibrating plate or a vibratory soil compactor. Here, the upper mass is essentially made up of the drive, for example an internal combustion engine or an electric motor. In addition, the upper mass can have further components, such as a fuel tank, a battery, control elements, covers, and a steering bar for steering the soil compacting device.
- The lower mass includes in particular the soil contact plate for compacting the soil and the imbalance exciter, which introduces the desired vibrations into the soil contact plate.
- The upper mass and the lower mass are movable relative to each other, so that under the influence of the vibrations the lower mass can move as freely as possible, while the upper mass should be decoupled as well as possible from the vibrations, and thus at rest. For this purpose, a vibration decoupling device is provided between the upper mass and the lower mass, for example a spring device or a spring-damper device. In practice, in particular rubber buffers have proven successful for the connection between the upper mass and the lower mass.
- The compensating coupling is provided at the system boundary between the lower mass and the upper mass, in particular at the location where the relative movement takes place between a shaft component mounted on the lower mass and a shaft component mounted on the upper mass. Because the compensating coupling is capable of compensating an axial offset, a radial offset, and an angular offset, it can compensate all the relative movements between the upper mass and lower mass.
- The drive shaft of the drive is to be understood broadly. The drive shaft is intended to be the output of the drive and can for example be connected downstream from a transmission appertaining to the drive, or from a centrifugal clutch also appertaining to the drive. In this way, the drive shaft can be realized as a solid shaft, but also as a hollow shaft or bell (e.g. in a centrifugal clutch).
- The various shafts indicated above, namely the drive shaft and the input shaft on the one hand and the output shaft and the exciter shaft on the other hand, can, if the compensating coupling is not to be connected between them, also be realized identical to one another, i.e. in particular can be made in one piece. Thus, it is not absolutely necessary for the two shaft elements situated opposite one another to be separate components. Rather, for example in a simpler design, the exciter shaft and the output shaft may be fashioned as a one-piece shaft.
- The bearer device performs a central function. Depending on the specific embodiment, it can be rigidly connected to the upper mass or to the lower mass, to one of the components provided there. For example, the bearer device on the lower mass can be fixedly or rigidly connected to the imbalance exciter and/or to the soil contact plate, thus forming a unit.
- The bearer device bears the input shaft and the output shaft and holds the two in a constant position relative to each other. In particular, the bearer device ensures that the input shaft and the output shaft have a constant shaft spacing, even during vibration operation, and run in the specified angular position, i.e. for example parallel to one another, or also at a right angle to one another. In this way, the problem that arises in vibratory soil compactors known from the prior art, of an axial spacing that constantly changes during vibrating operation, can be avoided. In this way, it is in particular ensured, as explained below, that for example two pulleys attached to the input shaft and the output shaft, and between which there runs a V-belt, always have the same axial spacing, with a high degree of parallel alignment. In this way, a long lifespan of the V-belt can be achieved.
- Due to its stiff, rigid design, the bearer device makes it possible for the transmission device that it bears to perform its intended function over the long term.
- The transmission device, and the torque-transmitting device provided in this connection, can be a belt drive or chain drive. It is also possible for the transmission device to be realized as a gear transmission or spur gear system.
- In a specific embodiment, the bearer device is fixedly connected to the upper mass. The compensating coupling is then provided between the output shaft of the transmission device and the exciter shaft of the imbalance exciter, the compensating coupling being designed to compensate an axial offset, a radial offset, and an angular offset between the output shaft and the exciter shaft.
- In this case, the bearer device is connected to the upper mass rigidly, or with a high degree of stiffness. The bearer device ensures the constant axial spacing between the input shaft and the output shaft coupled to the drive. The relative movement that then prevails during operation between the output shaft and the exciter shaft is compensated by the compensating coupling, so that the drive power can be transmitted from the output shaft to the exciter shaft.
- In another specific embodiment, the bearer device is connected to the lower mass fixedly or rigidly, i.e. with a high degree of stiffness. In this case, the compensating coupling is provided between the drive shaft of the drive and the input shaft of the transmission device, the compensating coupling then being designed to compensate an axial offset, a radial offset, and an angular offset between the drive shaft and the input shaft.
- In this alternative specific embodiment, the bearer device is thus attached to the lower mass, for example to the imbalance exciter, with a high degree of rigidity. Here as well, the bearer device is able to hold constant the axial spacing between the input shaft and the output shaft of the transmission device. In this way, the relative movement takes place between the drive shaft coming from the drive and the input shaft of the transmission device. The compensating coupling is situated there in order to compensate this relative movement.
- The bearer device and the transmission device can be at least partly enclosed by a transmission housing. In particular, it is advantageous if the components of the transmission device, in particular the torque-transmitting device, are enclosed largely completely by the transmission housing, and are thus encapsulated relative to the surrounding environment. For example, the transmission housing can be realized as a belt drive housing and can encapsulate the belt that transmits the torque from the surrounding environment.
- The transmission housing can have sheet elements that are fastened to the bearer device in order to form the housing. The bearer device can for example be fashioned as a cast part or welded part.
- The bearer device can be connected rigidly to the soil contact plate and/or to an exciter housing appertaining to the imbalance exciter.
- In this specific embodiment, it is advantageous if the input shaft is aligned with the drive shaft of the drive in an idle state of the soil compacting device. This means that the axes of rotation of the input shaft and the output shaft are aligned. In contrast, during vibration operation the rotational axes can assume a multiple offset (axial, radial, and angular), which is then compensated by the compensating coupling.
- The transmission device can be a belt drive having a first pulley and having a second pulley capable of being driven by the first pulley via a belt, for example a V-belt. The first pulley can be borne by the input shaft, while the second pulley can be borne by the output shaft. The exciter shaft of the imbalance exciter can be coupled to the output shaft, and thus to the second pulley, in such a way that it can be rotationally driven via the second pulley.
- If the transmission device is thus realized as a belt drive, the belt can be selected from the group: V-belt, toothed belt, V-ribbed belt. Alternatively, the transmission device can be realized as a chain drive or gear drive.
- The compensating coupling can be fashioned as a link coupling. Depending on the location at which the compensating coupling, or link coupling, is situated, the link coupling can have—if the compensating coupling, or link coupling, is situated between the drive shaft and the input shaft—a first crank that is coupled to the drive shaft, a second crank coupled to the input shaft, and a connecting rod that couples the first crank and the second crank, or—if the compensating coupling is situated between the output shaft and the exciter—the link coupling can have a first crank coupled to the output shaft, a second crank coupled to the exciter shaft, and a connecting rod coupling the first crank and the second crank.
- The first crank and the second crank can be rotated by an angle relative to one another that is bridged by the connecting rod. The respective coupling point at which the connecting rod is coupled to the respective shaft is then for example situated respectively at one end of a boom of the crank.
- The connecting rod can be pivotable by at least a small angle relative to the first crank and/or to the second crank. In particular, the connecting rod can be pivotable relative to the respective plane in which the respective crank is situated and rotates during operation. The connecting rod can be coupled to the first crank and/or to the second crank via an elastic bearing. With the aid of the elastic bearing, it is possible for the connecting rod to have the required ability to move relative to the first crank and to the second crank.
- The elastic bearing can be an elastomer spherical bearing. The spherical bearing can be made up of an inner metal sleeve that has a spherical surface and an outer metal sleeve that has a spherical bore. The two metal sleeves are fastened to the crank, or to the connecting rod, in such a way that no relative movement occurs between them, i.e. in the respective seat. Between the two metal sleeves there is in turn situated an elastomer, such as rubber, having the required elasticity. The elastomer spherical bearing can thus both twist and also deflect cardanically.
- The first crank and/or the second crank have a compensating mass situated, relative to their axis of rotation, opposite a coupling point to which the connecting arm is coupled. The compensating mass is used to compensate an imbalance that arises due to the coupling of the connecting rod to the boom of the respective crank. In this way, each crank can easily be balanced in itself together with the connecting rod coupled thereto.
- In a specific embodiment, a centrifugal clutch is provided as part of the drive, and the drive shaft is then part of the centrifugal clutch. The drive shaft can here for example be fashioned as a bell, or part of the bell of the centrifugal clutch. In this way, it is possible for the first crank to be connected directly to the drive shaft of the centrifugal clutch.
- According to the present invention, a bearer device is indicated that may be capable of being encapsulated by a housing, the device ensuring a defined axial distance between the input shaft and the output shaft, the two axes being capable of being held with a high degree of parallel alignment to one another. With the aid of the bearer or transmission housing, a clean environment, free of dust and foreign bodies, is ensured. Thus, in particular when the transmission device is realized as a belt drive, it is then possible for the life of the belt that is then used to exceed the assumed lifespan of the machine, and in this way long-term durability can be achieved.
- The relative movements that occur during operation between the upper mass and lower mass are expressed in that at the free end of the bearer device, or of the rigid transmission housing, or belt drive housing, achieved by the bearer device, relative movements occur that are compensated by the compensating coupling. If the compensating coupling is fashioned in the form of the link coupling, this coupling can compensate the offsets and transmit the power.
- These and further advantages and features of the present invention are explained in more detail below on the basis of examples, with the aid of the accompanying Figures.
-
FIG. 1A shows a highly schematized side view of a soil compacting device according to the present invention; -
FIG. 1B shows a rear view of the soil compacting device ofFIG. 1A ; -
FIG. 1C shows an enlarged detail ofFIG. 1B ; -
FIG. 2A shows a schematic side view of another specific embodiment of the soil compacting device; -
FIG. 2B shows a rear view of the soil compacting device ofFIG. 2A ; -
FIGS. 3A-3D show various views of a compensating coupling according to the present invention, as a link coupling; -
FIG. 4A shows a side view of an elastomer spherical bearing; -
FIG. 4B shows a sectional view of the elastomer spherical bearing; -
FIG. 5A shows a schematic side view of a soil compacting device according to the prior art; and -
FIG. 5B shows a rear view of the soil compacting device ofFIG. 5A . -
FIG. 1A (side view) andFIG. 1B (rear view) show a soil compacting device according to the present invention having anupper mass 1 that bears adrive 2, for example an internal combustion engine or an electric motor. Belowupper mass 1, alower mass 3 is provided that is coupled toupper mass 1 via a vibration decoupling device (not shown) and is movable relative to this upper mass.Lower mass 3 has asoil contact plate 4 and animbalance exciter 5 that during operation imparts a vibration tosoil contact plate 4. -
Imbalance exciter 5 can be constructed in a known manner. In particular,imbalance exciter 5 can have for example one or two imbalance shafts, not shown in the Figures, that can be set into rotational movement by the drive in order to bring about the desired vibrations for the soil compaction. - A guide handle 6 having a
control lever 7 is situated onupper mass 1. - Such a design of a vibrating plate is known from the prior art.
- For the transmission of the drive power from
drive 2 toimbalance exciter 5, abelt drive 8, acting as a transmission device, is provided.Belt drive 8 has various known components that are shown in the enlarged representation ofFIG. 1C . These are, in particular, a first pulley 9, situated in the upper region, asecond pulley 10, mounted in the lower region, and a V-belt 11 that circulates between first pulley 9 andsecond pulley 10. -
Belt drive 8 is held by abearer device 12 that is fastened rigidly toimbalance exciter 5, or to an exciter housing ofimbalance exciter 5. Alternatively,bearer device 12 can also be attached directly onsoil contact plate 4. -
Bearer device 12 is in particular a construction that is realized to be as stiff or rigid as possible, e.g. as a cast or welded part, in order to enable the bearing functions required bybearer device 12. - At the output of
drive 2 there is provided adrive shaft 13 that is aligned with aninput shaft 14 ofbelt drive 8. First pulley 9 ofbelt drive 8 is mounted oninput shaft 14. In the lower region,imbalance exciter 5 has anexciter shaft 15 that is aligned with anoutput shaft 16 ofbelt drive 8 and is coupled thereto.Exciter shaft 15 andoutput shaft 16 can also be realized in one piece as a shaft. -
Second pulley 10 ofbelt drive 8 is mounted onoutput shaft 16. - Because both
input shaft 14 andoutput shaft 16 are mounted inbearer device 12 together with first pulley 9 andsecond pulley 10, their axial spacing is held constant bybearer device 12. In addition, the parallel alignment ofinput shaft 14 andoutput shaft 16 is also maintained, including during operation. -
Belt drive 8 can form, together withbearer device 12, a belt drive housing, and can thus seal the belt drive running in the interior from the external environment. In this case, only two bores are then to be provided through which on the onehand input shaft 14 and on the otherhand output shaft 16 can extend. Because in this way a complete sealing of the belt drive housing inbearer device 12 can be achieved, no dust can penetrate. A penetration of dust can also be reduced through a corresponding fastening ofbearer device 12 to the exciter housing ofimbalance exciter 5. - Between drive
shaft 13 andinput shaft 14 there is provided a compensatingcoupling 17 that is used to compensate an axial offset, a radial offset, and an angular offset betweendrive shaft 13 andinput shaft 14, and which is further explained below. - For the sealing of the housing of
belt drive 8, alateral cover 18 can be fastened onbearer device 12.Cover 18 can be mounted with a seal. - The relative movements that occur during operation of
upper mass 1 andlower mass 3 are expressed in that the upper end ofbearer device 12, with the housing ofbelt drive 8, and thus inputshaft 14, comes closer to or moves away from the motor crankshaft or drive shaft 13 (axial offset), is displaced radially in all directions (radial offset), and that angular offsets occur between the two shafts (angular offset). Compensatingcoupling 17 compensates these offsets and transmits the drive power. -
FIGS. 2A and 2B show another specific embodiment of the vibrating plate. The essential design ofupper mass 1 andlower mass 3 is here identical to the specific embodiment ofFIGS. 1A-1C . - However, differing from the variant of
FIGS. 1A-1C , in the specific embodiment ofFIGS. 2A and 2B ,bearer device 12 is fastened fixedly or rigidly toupper mass 1. For example,bearer device 12 can be attached to the motor housing ofdrive 2. It is also possible to attachbearer device 12 to a bearing structure that is present onupper mass 1 but is not shown inFIGS. 2A and 2B . In any case, in thisway bearer device 12 moves together withupper mass 1, so that the corresponding relative movement betweenupper mass 1 andlower mass 3 is present at the lower end ofbearer device 12 onoutput shaft 16. Correspondingly, compensatingcoupling 17 is situated betweenoutput shaft 16 andexciter shaft 15. - If needed, compensating
coupling 17 can be protected against the penetration of rocks by a bellows. - In the variant of
FIGS. 2A and 2B , fewer movable components are situated onlower mass 3, which is strongly loaded with vibration, and this can improve the lifespan of these components. In addition,lower mass 3 is lighter, which can promote compacting power and can be favorable for the steering dynamics. - The design of compensating
coupling 17 can be seen inFIGS. 3A-3D , whereFIG. 3A shows the compensating coupling in a perspective view.FIG. 3B illustrates radial offset R,FIG. 3C shows an axial offset A, andFIG. 3D illustrates an angular offset W. - Compensating
coupling 17 has afirst crank 31 and asecond crank 32. First crank 31 is connected to second crank 32 via a connectingrod 33. Connectingrod 33 is pivotable relative to each of the twocranks FIG. 3B . In addition, connectingrod 33 is also pivotable about an axis that stands at an angle, e.g. perpendicular, to the shaft axes, in order to be able to execute the desired compensating movements (cf.FIGS. 3C and 3D ). - For this purpose, connecting
rod 33 is attached to a respective boom ofcrank spherical bearing 34, in particular an elastomer spherical bearing. - Compensating
coupling 17, fashioned as a link coupling, can operate both in pulling fashion and in pushing fashion. That is, first crank 31 can push connectingrod 33 in front of it in the direction of rotation, so that second crank 32 is pushed. Alternatively, first crank 31 can also rotate and draw connectingrod 33 in the direction of rotation, so that second crank 32 is drawn along by connectingrod 33 and follows the movement. -
Spherical bearing 34, fashioned as an elastomer spherical bearing, is shown in detail inFIGS. 4A and 4B , whereFIG. 4A shows a front view andFIG. 4B shows a vertical section. - Correspondingly, elastomer
spherical bearing 34 is made up of an inner metal sleeve 35 and anouter metal sleeve 36. Inner metal sleeve 35 has aspherical surface 37, whileouter metal sleeve 36 has aspherical bore 38. Betweenspherical surface 37 andspherical bore 38 there is situated anelastomer 39, for example rubber. - The two
metal sleeves 35, 36 are fastened to the respective crank 31, 32 and to connectingrod 33 in such a way that no relative movement occurs between the crank, or connecting rod, on the one hand, and the associated metal sleeve 35, 36 (cf. for exampleFIG. 3C ). In contrast, the relative movement takes place exclusively between the twometal sleeves 35, 36, and is absorbed byelastomer 39.Spherical bearing 34 can thus both twist (FIG. 4A ) and also deflect cardanically (FIG. 4B ). - So that the link coupling (compensating coupling 17) does not itself produce a strong imbalance, which in turn could have negative effects on the respectively affected roller bearings (not shown), on the
respective cranks 31, 32 a compensatingmass 40 is provided at the booms situated opposite the coupling points of connectingrod 33. Each of the compensatingmasses 40 extends into the coupling center, so that each coupling half, made up of one of thecranks spherical bearing 34, compensatingmass 40, respective fastening elements, and half of connectingrod 33, is always in itself balanced both statically and dynamically as long as the link coupling is not deflected. When there is a deflection of the link coupling, as a function of the deflection path there result smaller, subjectively imperceptible imbalance forces and corresponding resetting forces. - In the example shown in
FIGS. 1A-1C , first crank 31 is fastened ondrive shaft 13, or coupled thereto. Because it is entirely standard for a centrifugal clutch to be provided downstream fromdrive 2, so that during idling ofdrive 2 no torque is transmitted toimbalance exciter 5, and the centrifugal clutch closes, and the transmission of torque takes place, only when a particular rotational speed (switching rotational speed) is exceeded,drive shaft 13 can also be formed by a bell of the centrifugal clutch. In this case, first crank 31 can be attached directly on the bell (not shown in the Figures) of the centrifugal clutch (also not shown). - Second crank 32 is coupled to input
shaft 14 or is attached thereon. - When first crank 31 is set into rotational movement by
drive 2, this rotational movement is transmitted to second crank 32 via connectingrod 33. - When, due to the vibrating operation, the desired relative movement occurs between
upper mass 1 andlower mass 3, this movement can be compensated in compensatingcoupling 17. If, for example, the two shafts, namely driveshaft 13 andinput shaft 14, have an offset, then the two axes ofcranks cranks spherical bearing 34 is alternately twisted in a respective direction within a rotation. When there is an axial offset of the twocranks spherical bearing 34 is deflected cardanically. When there is an angular offset,spherical bearing 34 is alternately cardanically deflected within a rotation. - The maximum movements that occur during operation between
upper mass 1 andlower mass 3 are known to the manufacturer when designing a corresponding vibrating plate. From this, the maximum deflections of (elastomer)spherical bearing 34, and the frequency thereof, are ascertained, and in this way the spherical bearing can be designed so as to have long-term durability. In order to protect the spherical bearing against overloading in case of misuse, the offset betweenupper mass 1 andlower mass 3 can also be limited by stops. - In the specific embodiment of
FIGS. 2A and 2B , compensatingcoupling 17 is situated in the lower region betweenoutput shaft 16 andexciter shaft 15. In this case, first crank 31 can be attached tooutput shaft 16 and second crank 32 can be attached toexciter shaft 15. - The link coupling is not sensitive to contamination, in particular to abrasive dust, because neither sliding or rolling friction between two bodies takes place. The friction takes place only internally, within
elastomer 39. Only larger foreign bodies need be kept away from the link coupling, because at higher rotational speeds these are slung away and could thus present a danger. - In contrast to other known compensating couplings having a short constructive length, the link coupling offers a high transmissible torque in combination with comparatively high permissible offsets, in particular a high radial offset. All offsets can be increased continuously in all directions; aligned axes are also permissible. In addition, there is an insensitivity to dust, which is advantageous for the intended use of vibrating plates.
Claims (15)
1. A soil compacting device comprising:
an upper mass having a drive;
a lower mass connected to the upper mass so as to be movable relative thereto, and having a soil contact plate for soil compaction;
an imbalance exciter provided on the lower mass and capable of being driven by the drive;
a bearer device situated on one of the upper mass and the lower mass and connected fixedly thereto;
the bearer device bearing a transmission device having an input shaft and an output shaft that are coupled together by a torque-transmitting device for transmitting a torque from the input shaft to the output shaft;
the bearer device bearing the input shaft and the output shaft so that they are capable of rotation,
the drive having a drive shaft that is coupled to the input shaft;
the imbalance exciter having an exciter shaft that is coupled to the output shaft;
a compensating coupling being provided between the drive shaft of the drive and the input shaft of the transmission device or between the output shaft of the transmission device and the exciter shaft of the imbalance exciter; and
the compensating coupling being configured to compensate an axial offset, a radial offset, and an angular offset between one of 1) the drive shaft and the input shaft and 2) between the output shaft and the exciter shaft.
2. The soil compacting device as recited in claim 1 , wherein:
the bearer device is fixedly connected to the upper mass;
the compensating coupling is provided between the output shaft of the transmission device and the exciter shaft of the imbalance exciter; and
the compensating coupling is configured to compensate an axial offset, a radial offset, and an angular offset between the output shaft and the exciter shaft.
3. The soil compacting device as recited in claim 1 , wherein:
the bearer device is fixedly connected to the lower mass;
the compensating coupling is provided between the drive shaft of the drive and the input shaft of the transmission device; and
the compensating coupling is configured to compensate an axial offset, a radial offset, and an angular offset between the drive shaft and the input shaft.
4. The soil compacting device as recited in claim 3 , wherein the bearer device is rigidly connected to at least one of the soil contact plate and an exciter housing appertaining to the imbalance exciter.
5. The soil compacting device as recited in claim 1 , wherein the bearer device and the transmission device are at least partly enclosed by a transmission housing.
6. The soil compacting device as recited in claim 1 , wherein the input shaft is aligned with the drive shaft of the drive in an idle state of the soil compacting device.
7. The soil compacting device as recited in claim 1 , wherein:
the transmission device is a belt drive having a first pulley and a second pulley capable of being driven by the first pulley via a belt;
the first pulley is borne by the input shaft;
the second pulley is borne by the output shaft; and
the exciter shaft of the imbalance exciter is coupled to the output shaft and thus to the second pulley in such a way that is capable of being rotationally driven via the second pulley.
8. The soil compacting device as recited in claim 1 , wherein:
the compensating coupling is a link coupling that has:
a first crank that is coupled to the drive shaft;
a second crank that is coupled to the input shaft; and
a connecting rod that couples the first crank and the second crank; or
the compensating coupling is a link coupling that has:
a first crank that is coupled to the output shaft;
a second crank that is coupled to the exciter shaft; and
a connecting rod that couples the first crank and the second crank.
9. The soil compacting device as recited in claim 8 , wherein the first crank and the second crank are rotated by an angle relative to one another that is bridged by the connecting rod.
10. The soil compacting device as recited in claim 8 , wherein the connecting rod is pivotable relative to at least one of the first crank and the second crank by at least a small angle.
11. The soil compacting device as recited in claim 8 , wherein the connecting rod is coupled to at least one of the first crank and to the second crank via an elastic bearing.
12. The soil compacting device as recited in claim 11 , wherein the elastic bearing is an elastomer spherical bearing.
13. The soil compacting device as recited in claim 1 , wherein at least one of the first crank and the second crank has a compensating mass situated opposite, relative to their axis of rotation, a coupling point at which the connecting rod is coupled.
14. The soil compacting device as recited in one claim 1 , wherein:
a centrifugal clutch is provided as part of the drive; and
the drive shaft is part of the centrifugal clutch.
15. A soil compacting device comprising:
an upper mass having a drive;
a lower mass that is connected to the upper mass so as to be movable relative thereto and that has a soil contact plate for soil compaction;
an imbalance exciter that is provided on the lower mass and that is capable of being driven by the drive;
a bearer device that is situated on one of the upper mass and the lower mass and that is connected fixedly thereto; wherein
the bearer device bears a transmission device having an input shaft and an output shaft that are coupled together by a torque-transmitting device for transmitting a torque from the input shaft to the output shaft;
the bearer device bears the input shaft and the output shaft so that they are capable of rotation,
the drive has a drive shaft that is coupled to the input shaft;
the imbalance exciter has an exciter shaft that is coupled to the output shaft; and further comprising
a compensating coupling that is provided between one of 1) the drive shaft of the drive and the input shaft of the transmission device and 2) between the output shaft of the transmission device and the exciter shaft of the imbalance exciter, the compensating coupling being configured to compensate an axial offset, a radial offset, and an angular offset between one of 1) the drive shaft and the input shaft and 2) between the output shaft and the exciter shaft
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102017105117.1 | 2017-03-10 | ||
DE102017105117.1A DE102017105117A1 (en) | 2017-03-10 | 2017-03-10 | Soil compacting device with compensating coupling |
Publications (1)
Publication Number | Publication Date |
---|---|
US20180258601A1 true US20180258601A1 (en) | 2018-09-13 |
Family
ID=61563256
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US15/915,501 Abandoned US20180258601A1 (en) | 2017-03-10 | 2018-03-08 | Soil Compacting Device with Compensating Coupling |
Country Status (3)
Country | Link |
---|---|
US (1) | US20180258601A1 (en) |
EP (1) | EP3372729A1 (en) |
DE (1) | DE102017105117A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11359343B2 (en) * | 2019-04-05 | 2022-06-14 | Wacker Neuson Produktion GmbH & Co. KG | Control apparatus for soil compacting apparatus, with handlebar and rotational speed lever |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE202019101967U1 (en) | 2019-04-04 | 2019-07-02 | Ammann Schweiz Ag | Soil compactor with freewheel mode |
CN110044701B (en) * | 2019-04-29 | 2021-11-09 | 新疆维吾尔自治区交通规划勘察设计研究院 | Geosynthetic material construction damage testing device and method |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4113403A (en) | 1977-08-31 | 1978-09-12 | Stone Construction Equipment Inc. | Plate type compactor |
US5387052A (en) | 1993-03-09 | 1995-02-07 | M-B-W Inc. | Drive mechanism for a vibratory compactor |
DE102005013721B4 (en) | 2005-03-22 | 2014-12-24 | Siemens Aktiengesellschaft | Flexible all-steel multi-disc clutch |
DE102005029433A1 (en) | 2005-06-24 | 2006-12-28 | Wacker Construction Equipment Ag | Vibrating plate for compacting soil has one unbalanced mass not requiring phase adjusting device but all other unbalanced masses with such device |
DE102005036838B4 (en) * | 2005-08-04 | 2010-01-21 | Wacker Neuson Se | Mobile cutting device with vibration-insulated drive unit |
DE102008050676A1 (en) | 2008-10-07 | 2010-04-08 | Bald, Hubert, Dipl.-Ing. | Unbalances mass vibrator for exciting vibration of vibration table of concrete block machine, has mechanical element connected with unbalanced mass units as integral component or as separate component |
DE202010009261U1 (en) | 2010-06-18 | 2010-09-16 | Wacker Neuson Se | Vibration plate with V-belt calming |
EP2557327B1 (en) * | 2011-08-08 | 2015-10-14 | Centa-Antriebe Kirschey GmbH | Coupling unit for connecting a drive with an output |
-
2017
- 2017-03-10 DE DE102017105117.1A patent/DE102017105117A1/en not_active Withdrawn
-
2018
- 2018-03-05 EP EP18159888.9A patent/EP3372729A1/en not_active Withdrawn
- 2018-03-08 US US15/915,501 patent/US20180258601A1/en not_active Abandoned
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11359343B2 (en) * | 2019-04-05 | 2022-06-14 | Wacker Neuson Produktion GmbH & Co. KG | Control apparatus for soil compacting apparatus, with handlebar and rotational speed lever |
Also Published As
Publication number | Publication date |
---|---|
DE102017105117A1 (en) | 2018-09-13 |
EP3372729A1 (en) | 2018-09-12 |
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