EP4051852A1 - Drehantrieb zum verschwenken von zwei gelenkig miteinander verbundenen mastarmen - Google Patents
Drehantrieb zum verschwenken von zwei gelenkig miteinander verbundenen mastarmenInfo
- Publication number
- EP4051852A1 EP4051852A1 EP20804218.4A EP20804218A EP4051852A1 EP 4051852 A1 EP4051852 A1 EP 4051852A1 EP 20804218 A EP20804218 A EP 20804218A EP 4051852 A1 EP4051852 A1 EP 4051852A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- coupling
- rotary drive
- drive
- output gear
- movement
- 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
- 230000007246 mechanism Effects 0.000 claims abstract description 5
- 230000008878 coupling Effects 0.000 claims description 199
- 238000010168 coupling process Methods 0.000 claims description 199
- 238000005859 coupling reaction Methods 0.000 claims description 199
- 241000937413 Axia Species 0.000 claims 1
- 230000005540 biological transmission Effects 0.000 description 11
- 230000008859 change Effects 0.000 description 4
- 238000010276 construction Methods 0.000 description 4
- 238000006073 displacement reaction Methods 0.000 description 3
- 230000001360 synchronised effect Effects 0.000 description 3
- 238000006243 chemical reaction Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000009849 deactivation Effects 0.000 description 1
- 239000000428 dust Substances 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000002441 reversible effect Effects 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Classifications
-
- E—FIXED CONSTRUCTIONS
- E04—BUILDING
- E04G—SCAFFOLDING; FORMS; SHUTTERING; BUILDING IMPLEMENTS OR AIDS, OR THEIR USE; HANDLING BUILDING MATERIALS ON THE SITE; REPAIRING, BREAKING-UP OR OTHER WORK ON EXISTING BUILDINGS
- E04G21/00—Preparing, conveying, or working-up building materials or building elements in situ; Other devices or measures for constructional work
- E04G21/02—Conveying or working-up concrete or similar masses able to be heaped or cast
- E04G21/04—Devices for both conveying and distributing
- E04G21/0418—Devices for both conveying and distributing with distribution hose
- E04G21/0445—Devices for both conveying and distributing with distribution hose with booms
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/02—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member
- F15B15/04—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member with oscillating cylinder
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/02—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member
- F15B15/06—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member for mechanically converting rectilinear movement into non- rectilinear movement
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/02—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member
- F15B15/06—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member for mechanically converting rectilinear movement into non- rectilinear movement
- F15B15/061—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member for mechanically converting rectilinear movement into non- rectilinear movement by unidirectional means
Definitions
- the invention relates to a rotary drive for pivoting two articulated boom arms, as well as a concrete placing boom with a corresponding rotary drive.
- Stationary or mobile concrete pumps have a concrete distributor mast consisting of at least two articulated mast arms connected to one another via a pivot axis.
- the boom arms carry a concrete delivery line and can be extended by pivoting in such a way that different locations, for example on a construction site, can be reached through the placing boom. Due to the large range of the concrete placing boom, it is subject to heavy loads, which result essentially from the concrete delivery line running over the length of the placing boom and the concrete located therein. In particular, the articulated connections between the boom arms are exposed to high demands.
- the mast arms are usually driven by hydraulic cylinders and six-stroke gears.
- hydraulic cylinders and six-stroke gears are not only limited in terms of the joint angle, but allow the concrete delivery line to be carried out through the joint bolt only with curved and therefore heavy joint elements.
- Solutions with worm or gear drives are relatively heavy, which has a disadvantageous effect on the mass-performance ratio (power-to-weight ratio) of these drives.
- the object of the present invention is therefore to propose a Drehan drive for pivoting mast arms, in which the Known from the prior art disadvantages are avoided or at least reduced.
- the invention relates to a rotary drive for pivoting two articulated boom arms, in particular a concrete placing boom of a mobile or stationary concrete pump, with a transmission for conversion a translational piston movement into a rotary movement for the mast arm pivoting, the gear unit comprising a driven gear with a rotating coupling toothing and two hydraulically or electrically driven coupling elements, with at least one coupling element being in engagement with the coupling toothing of the driven gear.
- the invention also relates to a concrete placing boom with at least two articulated boom arms and a corresponding rotary drive for swiveling the boom arm, where a first boom arm is connected to the drive and a second boom arm is connected to the output gear, in particular via an output flange.
- the transmission enables the amount of movement to be changed starting from a translational piston movement to a rotary movement of the output gear.
- the gear unit has a drive (the translational piston movement to be changed) and an output (resulting rotary movement of the output gear).
- the drive on the one hand and the output on the other hand can each be connected to one of two mast arms that are articulated to one another.
- the position between the mast arms is maintained. If both coupling elements are in engagement with the coupling toothing, unwanted pivoting of the mast arms relative to one another can also be prevented in the event of deactivation of the rotary drive.
- the output gear has a circumferential coupling toothing on its outside or end face.
- the coupling toothing can extend over the entire circumference of the driven gear with evenly spaced teeth.
- the output gear can therefore essentially be designed as a hollow cylinder for the implementation of the concrete delivery line.
- a coupling element which is in engagement with the coupling teeth of the driven gear is in an engaged state.
- a coupling element that is not in engagement with the coupling teeth of the driven gear is decoupled from the driven gear and is in a disengaged state.
- a coupling element In order to drive the coupling element, it can be connected to a (hydraulic or electric) drive, for example via coupling rods.
- the invention is based on the knowledge that a Drehbe movement of the output gear can be created by means of two oppositely directed coupling elements that perform a substantially circular movement.
- a power transmission between the clutch element in engagement with the driven gear and the driven gear takes place when the clutch element moves in a straight line.
- the coupling elements are alternately engaged with the drive wheel and allow a rotary movement of the Output gear on the outward and return path of the translatory piston movement.
- a swivel angle is not limited (360 ° endless rotation).
- the coupling elements can also be driven with a comparatively short-stroke hydraulic cylinder, which leads to an improved power-to-weight ratio of the rotary drive compared to the prior art (long hydraulic cylinder).
- the delivery line can be guided through the rotary drive without the use of heavy articulated elements.
- the engaged coupling element can extend over a plurality of teeth of the coupling toothing, i.e. it can be in engagement with a plurality of teeth.
- the coupling element is thus fully seated on the output gear, which improves the active connection for power transmission between the output gear and the coupling element.
- the coupling element can be transferred between an engaged and disengaged state by moving the coupling element in the radial or axial direction.
- moving in the radial direction changes from the stand between the coupling element and an axis of rotation D of the driven gear.
- the coupling element moves in an axial direction its distance from the axis of rotation D remains constant and the coupling element is moved laterally out of the coupling teeth.
- the axial or radial movement of the coupling element can be followed by a separate drive.
- the movement of the coupling element in engagement with the driven gear in an essentially tangential direction is preferably converted into a rotary movement of the driven gear. puts.
- the implementation takes place accordingly to a rack and pinion gear, in which the straight movement of the rack leads to a rotary movement of the gear.
- a straight line and a circle have the same direction at the point of contact.
- the coupling elements can alternately, preferably alternately clocked, are in engagement with the output gear.
- the alternating engagement allows both forward and backward movements of a translatory movement of the coupling element to be converted into the rotary movement of the output gear, with only one of the coupling elements being allowed to be in engagement with the output gear.
- the direction of rotation of the rotary movement can be the same for both coupling elements.
- the rotary movement of the driven gear can take place gradually. With the gradual turning movement of the output gear, this can be locked in almost any position.
- a step-by-step rotation of the rotary drive can take place via a short-stroke hydraulic cylinder.
- the step-by-step control enables a high level of precision in the alignment, whereby the swivel angle is not limited (360 ° endless rotation).
- a complete cycle of the translational piston movement can correspond to a rotation of the output gear by a tooth spacing of the coupling teeth.
- the output gear rotates on the way there or back of the piston movement, each by half a tooth spacing in the same direction.
- the coupling elements can each be connected to a drive, preferably in an articulated manner, via a coupling rod. over the coupling rod results in a power transmission of the translatory piston movement of the drive to the coupling elements, which carry out a straight tangential movement. Due to the articulated arrangement, the coupling element can perform a rolling movement as a function of the position of the driven gear and can easily be brought into engagement with the coupling teeth.
- the drive comprises exactly one hydraulic cylinder which drives the two coupling elements by means of two coupling rods.
- This Ausry approximately form is particularly due to the lightweight construction in front of geous.
- the drive preferably comprises a hydraulic cylinder.
- the hydraulic cylinder is preferably designed as a double-acting hydraulic cylinder and / or more preferably as a plunger cylinder.
- the piston rod itself serves as a piston, which must, however, be guided axially.
- double-acting cylinders there are two opposing piston surfaces to which hydraulic fluid is applied. As a result, the cylinder has two active directions of movement.
- a coupling rod can be connected directly to the movable piston.
- the drive can be designed as an eccentric drive in which a Drehbewe movement of the eccentric is converted into a longitudinal movement.
- the eccentric drive can also be designed as an electric gear motor.
- the drive can take place via a lever drive in which a lever is connected to the piston rod.
- the rotary drive can also have a cam gear with a cam that can be rotated by a cam drive.
- the cam gear enables targeted control and transfer of the coupling elements between an engaged and disengaged state.
- the cam disk drive takes place separately from the drive.
- a change of the engaged coupling element can be carried out by means of the cam gear. This may, for example, be necessary between the forward and backward movement of the piston.
- the cam can also be used to improve the connection between the coupling element and the driven gear or to protect it from unintentional loosening.
- the cam disk can have at least one guide element for transferring the coupling element between the engaged and the disengaged state.
- the guide element can, for example, be designed as a guide groove which specifies a movement direction for the coupling element in the axial or radial direction.
- the first coupling element In one position of the cam, the first coupling element can be engaged and the second coupling element can be disengaged, and in another position of the cam, the first coupling element can be disengaged and the second coupling element can be engaged. With this cam, the engaged coupling element can thus be changed.
- both the first and the second coupling element are in an engaged position in an intermediate position. This ensures that at least one coupling element is always in engagement with the output gear.
- a hydraulic or hydrau lic-electrical control can be provided, which takes over both the control of the drive and the cam drive. Due to the interaction of the drive with the cam disk drive, the coupling elements can be moved precisely on opposite, essentially circular-like paths, in which an alignment of the coupling elements remains essentially unchanged.
- the circular path is not a pure circular path but is made up of movements of the coupling elements in tangential (translational piston movement) and radial / axial (transition between engaged and disengaged state).
- the coupling elements can each have an engagement or disengagement device, which is preferably formed by a hydraulic cylinder and a spring return device.
- an engagement or disengagement device which is preferably formed by a hydraulic cylinder and a spring return device.
- the transfer of the clutch elements can be controlled between the engaged and disengaged state.
- the coupling elements can each be designed as a tooth shoe.
- the toothing of the toothed shoes is preferably formed in such a way that the toothed shoes can be pressed onto the coupling toothing of the output gear and held with the least possible force.
- the toothing can have pawls that allow the tooth shoes to be radially lifted off even without cam gears or engaging or disengaging devices.
- the rotary drive can have a conical output gear or a drive gear with conical coupling teeth. Both options make it easier for an axially movable coupling element to transfer between the engaged and disengaged states.
- the coupling elements can each comprise a toothed ring lever and a driver element, at least one of the toothed ring levers being in engagement with the coupling teeth of the driven gear via the corresponding driver element.
- the toothed ring lever can be rotatably arranged parallel to the clutch toothing on the output gear and partially or fully constantly have a clutch toothing.
- the toothed ring levers can be driven by the drive.
- the Mit repertoireele elements can also have coupling teeth.
- a cam formed coaxially to the driven wheel with guide elements can be designed to transfer the driver elements between a release position and a locking position.
- the toothed ring lever In a release position, the toothed ring lever can rotate freely without any force being transmitted to the output gear.
- the toothed ring lever In the locked position, the toothed ring lever is in engagement with the coupling teeth of the driven gear, and power is transmitted to the driven gear from.
- the driver elements preferably have guide pins which engage in the guide elements in the form of guide grooves. Depending on the alignment / orientation of the cam, the driver elements can be moved axially.
- the rotary drive can have a housing which is designed coaxially with the output gear (and possibly the cam disk) and is mounted on the output gear.
- the housing protects the gear unit from dust, water and other foreign matter.
- Figures la-h a schematic representation of a rotary drive according to the invention according to a first embodiment in different operating states ah;
- FIG. 2 a schematic representation of a rotary drive according to the invention with separate drives according to a second embodiment
- FIG. 3 a schematic representation of a rotary drive according to the invention with an eccentric drive according to a third embodiment
- FIGS. 4a-4c a schematic representation of the rotary drive according to FIGS. La-h with a cam gear in various operating states;
- FIG. 5 a schematic representation of the rotary drive according to FIGS. 1 a-h with an engagement or disengagement device;
- FIG. 6 a schematic representation of a rotary drive according to the invention with a lever drive according to a fourth embodiment
- FIG. 7 a schematic representation of a rotary drive according to the invention with a lever drive according to a fifth embodiment
- FIG. 8 a schematic representation of a rotary drive according to the invention with separate drives and pawls according to a sixth embodiment
- FIG. 9 a schematic representation of a rotary drive according to the invention according to a seventh embodiment with axially movable coupling elements
- FIG. 10 a schematic sectional illustration of a rotary drive according to the invention with toothed ring levers and axially movable driver elements according to an eighth embodiment
- FIG. 11 a schematic representation of the rotary drive according to FIG. 10 with drive and cam disk drive;
- FIG. 12 a three-dimensional representation of the transmission of the rotary drive according to FIG. 10;
- FIG. 13 a three-dimensional representation of the transmission according to FIG. 12 without a cam disk
- FIG. 14 a three-dimensional representation of the transmission according to FIG. 13 without driver elements
- FIG. 15 a three-dimensional view of a rotary drive according to the invention built into an arm end of a mast arm according to a ninth embodiment.
- FIG. 16 a three-dimensional view of a rotary drive according to the invention according to a tenth embodiment. Based on the figures, the operating principle according to the invention is described below in the conversion of a translational piston movement into a rotary movement for a rotary drive 100 according to un different embodiments.
- Figures la to lh show a Drehan drive 100 according to the invention according to a first embodiment of the invention.
- the rotary drive 100 has a gear 20 and a drive 30.
- the drive 30 is preferably designed in the form of exactly one hydraulic cylinder 31, which is advantageous due to the light construction. In the figures la to lh the rotary drive is shown in various successive operating states.
- the transmission 20 has a drive wheel 22 with circumferential clutch teeth 24.
- the coupling teeth 24 extend on an outside of the output gear 22, the individual teeth of the coupling teeth 24 protruding in the radial direction with respect to the outside of the output gear 22.
- the coupling toothing 24 can also extend on one end face of the output wheel 22, the individual teeth of the coupling toothing 24 protruding in the axial direction with respect to the end face of the output wheel 22.
- the output gear 22 is mounted rotatably about an axis of rotation D.
- the output gear 22 is optionally in operative connection with a piston 32 of the hydraulic cylinder 31 via at least one of two coupling elements 26, 27 (upper coupling element 26 and lower coupling element 27), each with an articulated coupling rod 28, 29.
- the coupling elements 26, 27 are driven to.
- the coupling elements 26, 27 are designed as tooth shoes, ie with corresponding coupling teeth.
- the coupling elements 26, 27 are located above the coupling teeth Engagement with the coupling teeth 24 of the output gear 22.
- the coupling teeth 24 was chosen such that the coupling elements 26, 27 can be pressed onto the output gear 22 and held with the least possible radial force.
- the coupling elements 26, 27 lie flat on the output wheel (see FIG. 1 a), the engagement extending over several tooth distances.
- the drive 30 is formed as a hydraulic cylinder 31 in the form of a synchronous plunger cylinder (also double plunger cylinder).
- the piston rod itself serves as a piston 32 which, however, has to be guided axially.
- the volume of the incoming and outgoing hydraulic oil is always the same and the piston 32 moves back and forth at the same speed.
- the translatory cal direction of movement of the piston along the arrow directions shown in Figures la to lh takes place starting from the output gear 22 in a radial direction.
- the axis of rotation D of the output gear 22 and a central point of the piston 32, to which the coupling rods 28, 29 are attached, are essentially on one line.
- a power transmission between the coupling element 26, 27 in engagement with the output gear 22 and the output wheel 22 occurs when one of the coupling elements 26, 27 moves in a straight line Substantially circular movement performing coupling elements 26, 27.
- the opposing movement ste hen the coupling elements 26, 27 alternately with the drive gear 22 from and allow a rotary movement of the output gear 22 on the back and forth of the translational Piston movement.
- Figures la-d show the movement of the piston and the figures le-h show the return path of the piston movement.
- both the piston 32 of the hydraulic cylinder 31 and the output gear 22 are shown in a starting position.
- both coupling elements 26, 27 are in engagement with the coupling teeth 24 of the output gear 22.
- the drive wheel 22 is secured against rotation.
- the piston 32 has the greatest possible distance from the drive wheel 22 in the starting position. If a rotary movement of the output gear 22 is to be initiated, one of the clutch elements 26, 27 must first be transferred from the engaged to a disengaged state. The transfer of the clutch elements 26, 27 between the engaged and disengaged state can for example take place via a cam gear (not shown) with a cam disk and is explained in more detail below.
- the piston 32 is in an end position in which it has the smallest distance from the output gear 22.
- the piston 32 has moved again by half a cylinder length towards the driven gear 22, which again leads to a rotary movement of the driven gear 22 by a quarter tooth spacing of the coupling teeth.
- the upper coupling element 26 is still in an engaged state and the lower coupling element 27 is in the expressed state in which it is decoupled from the output gear 22.
- the output gear 22 is consequently rotated by one tooth spacing of the coupling toothing 24.
- the coupling elements 26, 27 have each carried out a substantially circular movement with mutually opposite directions of rotation.
- the drive wheel 22 moves from thus in each case by half a tooth spacing in the same direction.
- the coupling element 26, 27 is changed. The method can be repeated as desired, with either the upper or the lower coupling element 26, 27 being in engagement with the output gear 22 depending on the desired direction of rotation of the output gear 22.
- the piston oscillates in the cylinder, which makes the cylinder length independent of the total angle to be rotated.
- the drive 30 of the rotary drive 100 can also comprise two separate hydraulic cylinders 31 as an alternative to a single synchronous plunger cylinder.
- a movement of the coupling elements 26, 27 is controlled separately via the two hydraulic cylinders 31.
- the piston rod of the respective hydraulic cylinder 31 can function as a coupling rod 28, 29, which in turn is articulated with the coupling elements 26,
- the coupling elements 26, 27 are again as Trained tooth shoes.
- the mode of operation of the rotary drive 100 according to the second embodiment is, apart from this, unchanged from the mode of operation shown in Figures la-h.
- the pistons 32 of the two hydraulic cylinders 31 preferably move in unison.
- the drive 30 of the rotary drive 100 comprises an eccentric drive 33.
- the eccentric drive 33 a rotary movement of the eccentric (according to the arrow direction shown) is converted into a longitudinal movement.
- the eccentric drive 33 can also have an electric gear motor. This works as long as the longitudinal movement takes place in a direction that is radial with respect to the output gear 22.
- FIGS. 4a to 4c A rotary drive 100 according to the first embodiment with an additional cam gear is shown in FIGS. 4a to 4c.
- the cam mechanism comprises a cam disk 41 and a separate cam disk drive 42.
- the cam disk drive 42 is connected to the cam disk 41 in such a way that a movement of the piston 42 ′ in an essentially tangential direction causes the cam disk 41 to rotate.
- the cam disk drive 42 can be.
- the cam disk 42 is arranged essentially coaxially to the output gear 22 and has two guide grooves 43, 44 for guiding the coupling elements 26, 27.
- the coupling elements 26, 27 can, for example, engage the guide grooves 43, 44 via a projection not shown. According to FIGS. 4a to 4c, a change of the engaged coupling element 26, 27 with the aid of the cam gear is illustrated.
- the piston 42 'of the cam disk drive 42 is in a starting position.
- the cam 41 is rotated such that the upper coupling element 26 is in engagement with the output gear 22 and the lower coupling element 27 is decoupled from the output gear 22.
- the upper and lower coupling elements 26, 27 each engage in one of the guide grooves 43, 44 of the cam wheel 41.
- the guide grooves 43, 44 provide a different radial distance between the respective coupling element 26, 27 and the axis of rotation D of the output gear 22.
- the rotary drive 100 has two separate engagement and disengagement devices 50 instead of a cam gear.
- Each engagement or disengagement device 50 is assigned to one of the coupling elements 26, 27.
- the clutch elements 26, 27 are moved independently of one another in an essentially radial direction via the engaging and disengaging devices 50, which are designed as hydraulic cylinders 51, and are thus transferred between the engaged and disengaged states.
- the engagement and disengagement devices 50 are designed as hydraulic cylinders 51 with a spring return device 52.
- the spring return device 52 can be a tension spring which causes or promotes a transfer of the coupling elements 26, 27 from the engaged to the disengaged state.
- the embodiment of Figure 6 also has a drive 30 in the form of a lever drive, in which the coupling rods are not attached directly to a central position of the piston, but rather are arranged at the end of an additional lever rod.
- the coupling rods 28, 29 are no longer in the middle son countries laterally attached to the coupling elements 26, 27.
- the drive 30 additionally has a further lever 34 which extends transversely to the direction of movement of the piston. With the additional lever 34, it is no longer necessary to arrange the hydraulic cylinder 31 in a radial extension / alignment with the output gear 22.
- the A- or release devices 50 correspond to the embodiment shown in FIG. 6.
- a sixth embodiment of the rotary drive 100 which manages without an additional cam mechanism or an engagement or disengagement device.
- This Ausry approximately only serves to clarify the function of the rotary drive according to the invention, but is not to be given due to the comparatively heavy construction with four drives 30 and the associated complex control.
- four coupling elements 26, 26 ', 27, 27' are provided, each of which is connected via a coupling rod 28, 28 ', 29, 29' to a separately designed drive 30 in the form of a hydraulic cylinder 31.
- the drives 30 are each aligned essentially in a tangential direction with respect to the output gear 22.
- the hydraulic cylinders 31 each additionally have a compression spring for axial guidance.
- the coupling elements 26, 26 ', 27, 27' have coupling teeth with beveled teeth in the form of pawls. Depending on the direction of movement of the piston 32 (outward or backward), the toothed shoes engage positively in the coupling teeth 24 of the output gear 22 (outward) or can be easily detached from the coupling teeth 24 due to the bevel (return).
- spring return devices (not shown) for the hydraulic cylinder 31 are also provided.
- axially movable coupling elements 26, 27 are shown instead of radially movable coupling elements. It the coupling elements 26, 27 are toothed shoes.
- the output gear 22 preferably has a conical shape along the axis of rotation D or the teeth of the circumferential coupling toothing 24 have a conical shape along the axis of rotation.
- the coupling elements 26, 27 can be brought into engagement with the output gear 22 in a targeted manner by an axial displacement or decoupled from it.
- FIGS. 10 to 14 a rotary drive 100 according to an eighth embodiment with axially movable coupling elements 26, 27 is shown.
- the coupling elements 26, 27 each have a toothed ring lever 26a, 27a and a driver element 26b, 27b.
- the toothed ring levers 26a, 27a are arranged parallel to and spaced apart from the coupling teeth 24 on the output gear 22.
- the toothed ring levers 26a, 27a also each have a radially protruding section (see FIG. 12) to which a coupling rod (not shown) can be attached.
- the toothed ring levers 26a, 27a can thus be rotated via a drive 30.
- the toothed ring levers 26a, 27a have at least partially or completely a coupling toothing. Via the coupling teeth of the toothed ring levers 26a, 27a, the toothed ring levers 26a, 27a can be in engagement with the coupling teeth 24 of the output gear 22 via the driver element 26b, 27b.
- the slave elements 26a, 27b can also at least partially have coupling teeth.
- the driver elements 26b, 27b also engage on the rear side in a guide groove 43, 44 of a cam disk 41.
- the cam disk 41 is arranged coaxially to the output gear 22 and extends along the rotary axis D via both toothed ring levers 26a, 27a. Via the guide grooves 43, 44 in the cam disk 41, the driver elements 26b, 27b can be transferred between a release and a locked position.
- the toothed ring levers 26a, 27a are driven via the drive 30. Is the Mit supportiveele element 26b in engagement with the toothed ring lever 26a and the coupling toothing 24 of the output gear 22, the translatory cal piston reciprocating movement of the drive 30 is converted into a rotary movement of the Abriebrats 22 via toothed ring lever 26a and driver element 26b.
- the rotary drive 100 as shown in FIG. 11, additionally has a cam disk drive 42 with a movable piston 42 ′ for controlling the cam disk 41.
- the cam disk 41 which has an essentially hollow cylindrical shape, has at least two guide grooves 43, 44 which cause an axial displacement of the driver elements 26b, 27b, i.e. a displacement along the axis of rotation D.
- the cam disk 41 ensures that at least one driver element 26b, 27b is always in engagement with a toothed ring lever 26a, 26b and the coupling teeth 24 of the output gear 22.
- the driver elements 26b, 27b each have guide pins 26b ', 27b' projecting in the radial direction.
- the driver elements 26b, 27b engage in the guide groove 43 via the guide pins 26b ′, 27b ′ or 44 of the cam 41.
- the toothed ring lever 27a shown on the left in FIG. 13 is in an operative connection with the coupling toothing 24 of the output gear 22 (driver element 27b is in the locked position), while the right toothed ring lever 26a can rotate freely (driver element 26b is in the release position) .
- FIG. 14 only the output gear 22 with the two toothed ring levers 26a, 27a arranged adjacent to the clutch toothing 24 is shown.
- the ring gear levers 27a, 27b are slipped onto the output gear 22 and rotatably mounted on the output gear 22.
- a rotary drive 100 according to a ninth embodiment is shown in FIG.
- the rotary drive 10 is arranged in an arm end of a mast arm 10 which is part of a concrete placing mast 12.
- a further mast arm 10 '(not illustrated) can be connected to the illustrated arm end via an output flange arranged on the output gear 22.
- the pivoting of the mast arms 10, 10 ' can thus be controlled via the rotary drive 100.
- a drive of the Drehan drive 100 is within the box-shaped mast arm 10 is arranged.
- the rotary drive 100 has single-shear coupling rods 28, 29 which are connected to radially displaceable coupling elements 26, 27 (only coupling element 26 is visible in FIG. 15).
- the coupling element 26 has on both sides in the axial direction protruding guide pins, which are arranged adjacent to the coupling teeth 24 guide grooves 43,
- this has coupling rods 28, 29 consisting from several parallel to each other arranged coupling rod parts on. In the embodiment shown, he stretched a total of four coupling rod parts between more sleek bolts. In comparison to the embodiment shown in FIG. 15, the coupling points are displaced outwards above or below the hydraulic cylinder. Via the coupling rods 28, 29, the radial displaceable coupling elements 26, 27 are driven, which in turn engage in guide grooves 43, 43 ', 44, 44' of the cam disks 41, 41 'via protruding guide pins 26', 27 '.
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Abstract
Description
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Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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DE102019135680.6A DE102019135680B3 (de) | 2019-12-23 | 2019-12-23 | Drehantrieb zum Verschwenken von zwei gelenkig miteinander verbundenen Mastarmen |
PCT/EP2020/081449 WO2021129973A1 (de) | 2019-12-23 | 2020-11-09 | Drehantrieb zum verschwenken von zwei gelenkig miteinander verbundenen mastarmen |
Publications (2)
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EP4051852A1 true EP4051852A1 (de) | 2022-09-07 |
EP4051852B1 EP4051852B1 (de) | 2024-07-31 |
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EP20804218.4A Active EP4051852B1 (de) | 2019-12-23 | 2020-11-09 | Drehantrieb zum verschwenken von zwei gelenkig miteinander verbundenen mastarmen |
Country Status (3)
Country | Link |
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EP (1) | EP4051852B1 (de) |
DE (1) | DE102019135680B3 (de) |
WO (1) | WO2021129973A1 (de) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
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CN115354860A (zh) * | 2022-09-22 | 2022-11-18 | 三一汽车制造有限公司 | 臂架控制***、臂架控制方法及车辆 |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2648416A (en) * | 1950-09-11 | 1953-08-11 | Be Ge Mfg Co | Reversible clutch for hydraulic power mechanism |
DE971756C (de) * | 1953-01-15 | 1959-03-26 | Gewerk Eisenhuette Westfalia | Klinkenschaltwerk, insbesondere fuer den Antrieb des Fahrwerks von Lademaschinen |
US2947317A (en) * | 1953-06-12 | 1960-08-02 | Electraulic Presses Ltd | Unloading valves for hydraulic pumps |
US3515009A (en) * | 1967-06-24 | 1970-06-02 | Braunschweigische Masch Bau | Drive for rotary bodies having large dimensions and great weight |
US8863966B2 (en) * | 2011-03-21 | 2014-10-21 | Dynaking Crane, Llc | Kingpost crane apparatus and method |
CN202176115U (zh) * | 2011-06-13 | 2012-03-28 | 北汽福田汽车股份有限公司 | 折叠式臂架、折叠式臂架装置和混凝土泵车 |
AT511833B1 (de) * | 2011-11-10 | 2013-03-15 | Schwing Gmbh F | Mastaufbau insbesondere für eine autobetonpumpe |
DE102018104491A1 (de) * | 2018-02-27 | 2019-08-29 | Putzmeister Engineering Gmbh | Großmanipulator mit Schwingungsdämpfer |
-
2019
- 2019-12-23 DE DE102019135680.6A patent/DE102019135680B3/de active Active
-
2020
- 2020-11-09 WO PCT/EP2020/081449 patent/WO2021129973A1/de unknown
- 2020-11-09 EP EP20804218.4A patent/EP4051852B1/de active Active
Also Published As
Publication number | Publication date |
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WO2021129973A1 (de) | 2021-07-01 |
DE102019135680B3 (de) | 2020-12-10 |
EP4051852B1 (de) | 2024-07-31 |
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