EP3128275A1 - Zementklinkerkühlrost - Google Patents

Zementklinkerkühlrost Download PDF

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Publication number
EP3128275A1
EP3128275A1 EP15180131.3A EP15180131A EP3128275A1 EP 3128275 A1 EP3128275 A1 EP 3128275A1 EP 15180131 A EP15180131 A EP 15180131A EP 3128275 A1 EP3128275 A1 EP 3128275A1
Authority
EP
European Patent Office
Prior art keywords
conveying means
grate
reciprocating
reciprocating conveying
motor
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
Application number
EP15180131.3A
Other languages
English (en)
French (fr)
Other versions
EP3128275B1 (de
Inventor
Jörg Hammerich
Martin Deutgen
Peter Hennemann
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Alite GmbH
Original Assignee
Alite GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Alite GmbH filed Critical Alite GmbH
Priority to EP15180131.3A priority Critical patent/EP3128275B1/de
Priority to ES15180131.3T priority patent/ES2669005T3/es
Priority to DK15180131.3T priority patent/DK3128275T3/en
Publication of EP3128275A1 publication Critical patent/EP3128275A1/de
Application granted granted Critical
Publication of EP3128275B1 publication Critical patent/EP3128275B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F27—FURNACES; KILNS; OVENS; RETORTS
    • F27D—DETAILS OR ACCESSORIES OF FURNACES, KILNS, OVENS, OR RETORTS, IN SO FAR AS THEY ARE OF KINDS OCCURRING IN MORE THAN ONE KIND OF FURNACE
    • F27D15/00—Handling or treating discharged material; Supports or receiving chambers therefor
    • F27D15/02—Cooling
    • F27D15/0206—Cooling with means to convey the charge
    • F27D15/0213—Cooling with means to convey the charge comprising a cooling grate
    • F27D15/022—Cooling with means to convey the charge comprising a cooling grate grate plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F27—FURNACES; KILNS; OVENS; RETORTS
    • F27B—FURNACES, KILNS, OVENS, OR RETORTS IN GENERAL; OPEN SINTERING OR LIKE APPARATUS
    • F27B7/00—Rotary-drum furnaces, i.e. horizontal or slightly inclined
    • F27B7/20—Details, accessories, or equipment peculiar to rotary-drum furnaces
    • F27B7/38—Arrangements of cooling devices
    • F27B7/383—Cooling devices for the charge
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F27—FURNACES; KILNS; OVENS; RETORTS
    • F27B—FURNACES, KILNS, OVENS, OR RETORTS IN GENERAL; OPEN SINTERING OR LIKE APPARATUS
    • F27B7/00—Rotary-drum furnaces, i.e. horizontal or slightly inclined
    • F27B7/20—Details, accessories, or equipment peculiar to rotary-drum furnaces
    • F27B7/42—Arrangement of controlling, monitoring, alarm or like devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F27—FURNACES; KILNS; OVENS; RETORTS
    • F27D—DETAILS OR ACCESSORIES OF FURNACES, KILNS, OVENS, OR RETORTS, IN SO FAR AS THEY ARE OF KINDS OCCURRING IN MORE THAN ONE KIND OF FURNACE
    • F27D19/00—Arrangements of controlling devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F27—FURNACES; KILNS; OVENS; RETORTS
    • F27D—DETAILS OR ACCESSORIES OF FURNACES, KILNS, OVENS, OR RETORTS, IN SO FAR AS THEY ARE OF KINDS OCCURRING IN MORE THAN ONE KIND OF FURNACE
    • F27D21/00—Arrangements of monitoring devices; Arrangements of safety devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F27—FURNACES; KILNS; OVENS; RETORTS
    • F27D—DETAILS OR ACCESSORIES OF FURNACES, KILNS, OVENS, OR RETORTS, IN SO FAR AS THEY ARE OF KINDS OCCURRING IN MORE THAN ONE KIND OF FURNACE
    • F27D15/00—Handling or treating discharged material; Supports or receiving chambers therefor
    • F27D15/02—Cooling
    • F27D15/0206—Cooling with means to convey the charge
    • F27D15/0213—Cooling with means to convey the charge comprising a cooling grate
    • F27D15/022—Cooling with means to convey the charge comprising a cooling grate grate plates
    • F27D2015/0226—Support, fixation of the grate

Definitions

  • the invention relates to a cement clinker cooler grate for cooling and conveying cement clinker in a forward direction comprising a grate surface for supporting the clinker, which may be unloaded from a kiln onto said grate surface.
  • the clinker is conveyed by some reciprocating conveying means, e.g. a reciprocating row of grate plates, being arranged one besides of the other on a reciprocating cross beam.
  • the reciprocating conveying means is driven by an actuator being operably connected to the reciprocating conveying means for driving the reciprocating conveying means.
  • the invention as well relates to a method for driving the reciprocating conveying means of a cement clinker cooler grate.
  • cement clinker manufacturing raw meal is burnt and sintered in a rotary kiln to thereby obtain cement clinker, briefly 'clinker' which may subsequently be further processed to obtain cement.
  • the clinker is unloaded from said kiln via the so called clinker inlet distribution system, as well referred to as clinker distribution system, onto a conveyor grate floor of a clinker cooler, briefly 'cooler'.
  • the clinker inlet distribution system often resembles a chute.
  • the clinker forms a layer, as well referred to as clinker bed.
  • the height of the clinker bed is typically about 0.5m-0.7m.
  • the clinker bed is cooled and transported (conveyed) in a forward direction to a clinker outlet of the cooler, e.g. via a crusher for further processing, e.g. milling.
  • the construction of the grate floor is essential as on the one hand cooling air has to be inserted into the clinker bed via the grate floor and on the other hand clinker drop through the grate floor has to be avoided.
  • the clinker has to be transported and the grate floor must withstand the high clinker temperatures and the abrasion caused by moving the clinker over the grate floor.
  • coolers have a grate surface with grate openings for injecting a cooling gas via the grate into the clinker residing on top of the grate. Further, these coolers have conveying means for conveying the clinker in said forward direction. There are multiple conveying systems, the most common systems come under one of the following categories:
  • the problem to be solved by the invention is to provide a clinker cooler with reciprocating conveying means that is easier to manufacture and easier to maintain and has lower operation expenses.
  • the cement clinker cooler grate enables conveying clinker or another bulk material in a conveying direction.
  • the conveying direction or forward direction is directed from the clinker inlet, i.e. the kiln facing side of the clinker cooler to its clinker outlet.
  • the cooler further comprises a conveyor grate, briefly 'grate', with an up facing surface for supporting the clinker.
  • the grate may comprise planks being arranged one besides of the other with their longitudinal direction in parallel to the conveying direction. At least one, preferably some of the planks may be movably supported to enable a reciprocating movement parallel to the conveying direction. In other words at least some of the planks can be moved forward and retracted afterwards.
  • the grate is a step grate, which comprises overlapping rows providing a stepped grate surface. These rows are often formed by grate plates being arranged transverse to the conveying direction e.g. on cross beams, wherein at least some of the grate plates are movably supported to enable a reciprocating movement of the respective grate plates.
  • the movable planks are reciprocating conveying means and in the second example, the movable grate elements are reciprocating conveying means.
  • a further example for a reciprocating conveying means could be a cross bar being movably supported to reciprocate parallel to the conveying direction above a static grate surface.
  • the reciprocating movement can be, but is not necessarily a linear movement.
  • Some suspensions of reciprocating conveying means are pendulum suspensions providing a small vertical amplitude. Such movement is considered as 'quasi linear', i.e. almost linear.
  • reciprocating conveying means are not lowered, i.e. not moved downwards below the grate to enable retraction as it is the case for circulating conveying means of chain conveyors, drag-chain conveyors and belt conveyors.
  • the cooler comprises at least one actuator being operably connected to at least one reciprocating conveying means for driving the reciprocating conveying means.
  • the actuator comprises at least one electric motor with a rotor being mechanically connected to the reciprocating conveying means for driving said conveying means by a transmission.
  • 'mechanically connected' means that the connection enables to transfer a rotation of the rotor into a reciprocating movement of at least one reciprocating conveying means, e.g. by a crank mechanism explained below.
  • hydraulic or pneumatic actuators are preferably not considered as a mechanical connection.
  • the grate cooler further comprises at least one controller being electrically connected to the electric motor for controlling the rotational speed of its rotor as a function of the position and/or direction of movement of the reciprocating conveying means.
  • the controller thus preferably comprises at least one sensor for sensing the position of the at least one reciprocating conveying means and controls the rotational speed of the motor preferably in a closed loop as a function of said position.
  • the invention is based on the observation that hydraulic drives often suffer from leaking and the risk of oil contamination due to leaks.
  • the solution of the invention is much simpler, hydraulic lines, aggregates etc. are completely omitted.
  • hydraulic drives are mostly expensive, not only in acquisition but as well in maintenance and in particular in operation due to their low efficiency and the fact that the recent developments in power electronics enable to precisely control the speed of the reciprocating conveying means.
  • 'mechanical connection' i.e. said transmission can be provided e.g. by at least one crank or eccentric shaft (both commonly referred to as 'crank'), being driven by the rotor, preferably via at least one gear.
  • a connecting rod may be connected by a first pivot with a first pivot point to said crank and via a second pivot with a second pivot point to the at least one reciprocating conveying means.
  • the latter connection is not necessarily a direct connection, for example the reciprocating conveying means may be connected to the connection rod via some force transmitting means, e.g. a drive frame coupling the connection rod to said at least one reciprocating conveying means or a cross bar supporting the reciprocating conveying means.
  • the first and second pivots each have a pivot point or a pivot axis, briefly commonly referred to as first or second pivot point, respectively.
  • two or more motors may be connected to a drive shaft.
  • each motor may drive a reduction gear with an output shaft which is coupled to the drive shaft.
  • Said drive shaft drives at least one, preferably two or more cranks.
  • Said cranks are coupled each by at least one connection rod to at least one reciprocating conveying means.
  • two or more motors may commonly drive a drive shaft which is connected to two or more crank drives. This design enhances longevity as the load is shared between multiple redundant parts. Alternatively the load, i.e. the maximum power that can be coupled to the reciprocating conveying means can be enhanced.
  • the mechanical connection is thus a transmission for converting the rotation provided by the motor into a linear movement of the reciprocating conveying means.
  • T can be varied to augment the conveying speed of the clinker: decreasing the period T will augment the clinker speed and increasing T will slow the clinker down. Only for simplicity, it is assumed that T is constant, as the conveying speed is adjusted in response to changes of the clinker production rate. This assumption typically holds true for time scales being much longer than the period T.
  • the sensor can be e.g. a sensor measuring the angular position ⁇ of the crank arm, i.e. the direction of the vector pointing from the rotational axis of the crank to the pivot point of the first pivot.
  • the rotational direction of the motor is constant. This simplifies the controller's electronics and enhances the longevity of the mechanical components of the transmission.
  • the first pivot and/or at least a part of said connecting rod are positioned below a clinker inlet distribution chute.
  • This enables to arrange the connecting rod's longitudinal axis at least approximately parallel ( ⁇ 30°) to the direction of movement of the reciprocating conveying means.
  • the connecting rod's inclination changes when the crank rotates, but here the mean inclination shall define the rod's longitudinal axis.
  • the rod's inclination is to be measured when the crank arm's longitudinal axis is parallel to the moving direction of the reciprocating conveying means.
  • This essentially parallel orientation of the connection rod and the conveying direction enables to keep the vertical components of the drive force low and thus the additional load to be compensated, e.g.
  • connection rod can be even longer, if the crank and thus the pivot are positioned in the extension of the clinker inlet distribution system, e.g. between the clinker inlet distribution system and a base supporting bearings for the kiln. Accordingly, the distance d pp between the first pivot point and the second pivot point is at least 10 times bigger than the distance d pa between the first pivot's pivot point and the rotational axis of the crank, i.e. d pp ⁇ 10 ⁇ d pa or even better d pp ⁇ 20 ⁇ d pa , preferably d pp ⁇ 30 ⁇ d pa .or even d pp ⁇ 50 ⁇ d pa .
  • the grate is typically supported on a base by a static frame below said grate.
  • Said frame may as well support the electric motor and/or a gear coupling the motor with the crank or a connection rod, or in other words, the electric motor and/or the gear may be attached to said frame.
  • This mounting point has the advantage that the counter action of the driving force for driving the reciprocating conveying means is directly absorbed by the frame.
  • the motor may drive the crank via a reduction gear with an output shaft.
  • the motor may be attached to and be supported by the gear, e.g. its housing.
  • the output shaft is preferably coupled by a releasable coupling to the crank, e.g. via a drive shaft.
  • the crank and/or the drive shaft, respectively may support the gear (and thus the motor as well) vertically, i.e. their weight.
  • the frame may comprise a torque support supporting the gear.
  • a beam of the frame may comprise a torque support blocking a rotation of the gear housing in at least one direction.
  • at least one flange of a beam may provide said torque support.
  • Decoupling of torque and weight support enables to easily replace a worn gear by simply removing the gear from the drive shaft or crank, respectively and replacing it by pushing a new gear onto the drive shaft or crank.
  • the output shaft is a hollow shaft being form fittingly received by the corresponding end of the drive shaft (or vice versa).
  • the releasable coupling enables to simply pull the gear off the drive shaft and to connect a new one by literally pushing it on the drive shaft.
  • the frame may of course comprise a bearing supporting the crank and/or the drive shaft and thus the weight of the gear (and the motor) via said bearing. But in any case weight and torque support are obtained differently, enabling to repair the grate in short term.
  • the rotor rotates at a constant rotational speed.
  • the speed of the conveying means is sinusoidal. This sinusoidal speed of the conveying means already provides advantages with respect to the longevity of the bearings, because the peaks in the force transmitted between the motor and the reciprocating conveying means are reduced if compared with the prior art hydraulic actuated reciprocating conveying means.
  • the controller is configured to monitor at least the direction of movement of the reciprocating conveying means and to change the rotational speed of the motor as a function of the direction of movement of the reciprocating conveying means.
  • the controller may be configured to speed up the motor, i.e. to augment the rotational speed of its rotor when retracting the conveying means and to slow the motor down (i.e. to reduce the rotational speed) when pushing the conveying means forwards.
  • the controller may be configured to vary the rotational speed of the motor as a function of the angular position ⁇ of the crank arm between preferably at least two constant values: a first value ⁇ f,const defining a first absolute value of a first constant rotational speed of the motor during the forward movement of reciprocating conveying means and a second value ⁇ r,const defining a second absolute value of a constant rotational speed of the motor during the retraction of the reciprocating conveying means. At least one of said values ⁇ f,const ⁇ r,const is preferably maintained for a significant period of the forward or backward movement, respectively, of the reciprocating conveying means.
  • the rotational speed of the motor ⁇ f,const during the forward movement of reciprocating conveying means is preferably smaller than the corresponding rotational speed during retraction ⁇ r,const, i.e. ⁇ f,const ⁇ ⁇ r,const , more preferred: 1.5 ⁇ ⁇ f,const ⁇ ⁇ r,const , or better: 2 ⁇ ⁇ f,const ⁇ ⁇ r,const or even 3 ⁇ ⁇ f,const ⁇ ⁇ r,const .
  • the force F r required for retracting the conveying means is essentially constant d F r d ⁇ r ⁇ 0 , but the force F f for driving the reciprocating conveying means forward increases with ⁇ f .
  • speeding up the retraction speed does not (significantly) increase the force to be transmitted by the transmission and thus not the maintenance costs (strictly per cycle), but it enables to shorten the period T of a cycle.
  • ⁇ f,const can be minimized and ⁇ r,const can be maximized for a given required conveying speed of the clinker to thereby reduce the mean load of the transmission.
  • ⁇ f,const upon a request for augmenting or reducing the clinker conveying speed preferably only ⁇ f,const is augmented or reduced, respectively as ⁇ r,const should be kept at least almost constant close to its designed maximum, as it should always be as large as reasonable.
  • the change in ⁇ r,const for change of the conveying speed ⁇ r,const is preferably smaller than 50% of the corresponding change in ⁇ f,const when changing the conveying speed, i.e.
  • ⁇ r,const ⁇ 0.5 ⁇ ⁇ ⁇ f,const , preferably ⁇ ⁇ r,const ⁇ 0.25 ⁇ ⁇ ⁇ f,const or even better ⁇ ⁇ r,const ⁇ 0.1 ⁇ ⁇ ⁇ f,const .
  • the controller is preferably configured to restrict the torque M provided by the motor to the crank arm when the crank arm passes its dead centers (at least one of the two dead centers) to a preselected value M s .
  • This preselected value can be e.g. 150% of the torque value M f,max or M r , max required for pushing the reciprocating conveying means in the forward or rearward direction, respectively, with maximum forward or backward (respectively) speed during a cycle i.e., M s ⁇ 1.5 ⁇ M f,max or M s ⁇ 1.5 ⁇ M r,max , M s ⁇ M f,max or M s ⁇ M r,max , preferably M s ⁇ 0.8 ⁇ M f,max or M s ⁇ 0.8 ⁇ M r,max or even smaller.
  • the direction of movement of the reciprocating conveying means is inverted.
  • This inversion provides a high load or stress in particular to the bearings, e.g. said at least one pivot; restricting the torque reduces the speed of the motor and thus of the reciprocation conveying means when passing the dead centers, but avoids load peaks and thereby reduces maintenance costs.
  • the controller may preferably be configured to control the rotational speed of the motor and thus of the crank arm to ramp up the forward speed v f of the reciprocating conveying means to a maximum value v f,max and to maintain this maximum value v f,max until the reciprocating conveying means is to be slowed down ('ramp down') prior to retracting the respective reciprocating conveying means.
  • the motor's rotational speed is controlled to compensate for a nonlinear transmission.
  • the controller may thus compensate the sinusoidal relationship between the speed of the conveying means and the crank arm's angular position.
  • the ramp up of the forward speed is preferably at least essentially linear, or has at least a linear section. Under the assumption that the coupling between the conveying means and the clinker on top of the grate is constant for the corresponding speed of the reciprocating conveying means this results in a constant load to the bearings like e.g. said pivots, during ramp up and thus reduced maintenance costs.
  • the ramp down of the at least one conveying means' forward speed is preferably steeper than the ramp up of the forward speed.
  • 'steeper' refers to the absolute value of the mean slope.
  • a very simple measure is the time for ramp up and the time for ramp down: The ramp up time of the forward speed is preferably bigger than the ramp down time of the forward speed.
  • Retraction of the conveying means may be controlled by the controller in a similar manner.
  • the absolute value of the maximum retraction speed v r,max is preferably higher than the absolute value of maximum forward speed v f,max , e.g. 1.5 ⁇ v f,max ⁇ V r,max even more preferred 2 ⁇ v f,max ⁇ v r,max or even 3 ⁇ v f,max ⁇ v r,max .
  • the relative amount of time during retraction where v r,max is maintained is preferably smaller that the relative amount of time where v f,maX is maintained, i.e.
  • a method for controlling the velocity v(t) of at least one reciprocating conveying means of a cement clinker cooler grate may comprise actuating the reciprocating conveying means by powering an electric motor.
  • said electric motor may have a rotor being coupled via at least a crank and a connection rod to the least one reciprocating conveying means.
  • the rotational speed of the motor may be controlled to linearize the movement of the conveying means.
  • the rotational speed may be controlled as a function of the crank's spatial orientation, i.e. its angular position.
  • the motor is coupled via a reduction gear to a drive shaft.
  • the drive shaft drives and optionally supports the crank.
  • a sinusoidal movement of the crank in the direction of the reciprocating movement is compensated at least partially.
  • ⁇ angular velocity
  • a simple controller controlling the rotational speed of the motor's rotor which drives the crank arm, preferably with a fixed reduction ratio due to some reduction gear, thus enables to reciprocate the reciprocating conveying means with almost any velocity profile and in particular to compensate the sinusoidal movement of the pivot point.
  • the absolute value of the slope of the velocity v t i . e . d d t v t of the reciprocating conveying means has at least a local minimum when the velocity v (t) changes its sign.
  • the maximum angular speed of the crank when retracting the at least one reciprocating conveying means is bigger than the maximum angular speed of the crank when pushing said at least one reciprocating conveying means. This can as well be obtained by adjusting the rotational speed of the motor accordingly.
  • Cement clinker may be unloaded from a kiln 90 onto a clinker inlet distribution system 5.
  • the clinker distribution system 5 is a chute of overlapping grate plates 50 being mounted one besides of the other on cross beams 55.
  • the cross beams may be supported by at least one girder 57.
  • Other types of clinker distribution systems may be used as well.
  • the grate plates 50 or at least some of them provide cooling slits 59 for blowing a cooling gas from below the grate plates 50 into the clinker on top of them. From this clinker inlet distribution system, the clinker is supplied to a cement clinker cooler grate 1, briefly 'grate'.
  • This grate 1 comprises grate plates 30, 35 on cross beams 31, 36.
  • multiple grate plates 30, 35 are arranged one besides of the other on a cross beam 31, 36.
  • a row of grate plates 30, 35 overlaps the next row (referring to the conveying direction 2) thereby providing a step grate with a grate surface 4.
  • At least one of the grate plates 30, 35 is movably supported, enabling a reciprocating movement as indicated by double headed arrows 3.
  • the corresponding cross beams 36 are movably supported on longitudinal extending guide rails 37 or girders 37, but other solutions for movably supporting the reciprocating cross bars 36 are as well possible.
  • the movable support is simplified as slide bearing, other types of movable supporting the reciprocating conveying means are possible as well, for example the pendulum support as disclosed in DE 101 18 440 or the ball bearing support suggested in DE 1841381 to name only two.
  • An actuator is provided for pushing the movable grate plates 35 forward and to retract them afterwards.
  • the clinker is pushed in the forward direction 2.
  • the grate plates 35 are retracted and the front plates of the respective (previous) overlapping fixed grate plates 30 inhibit the clinker bed to be retracted as well.
  • the movable grate plates 35 thus slide below the clinker bed when retracted.
  • the movable grate plates 35 are thus reciprocating conveying means.
  • the actuator comprises an electric motor 10 driving a drive shaft 11, e.g. via a reduction gear.
  • the stator of the electric motor 10 and the optional reduction gear are preferably mounted to the frame supporting the clinker cooler on its base 9.
  • the frame may comprise vertical beams ('poles') 51, 52, girders 37, 57, cross beams 55, 31 and the like.
  • the drive shaft 11 is mechanically coupled to a crank arm 15.
  • the crank arm 15 is connected via pivot 16 with at least one connection rod 20.
  • the at least one connection rod 20 is attached as well to a reciprocating conveying means 35.
  • the reciprocating conveying means 35 is connected to the connection rod 20 via the movably supported cross beam 36 and a further pivot 19.
  • An optional transmission rod 22 may connect further reciprocating conveying means 35.
  • a transmission rod 22, may e.g. be a longitudinal beam of a movably supported drive frame, to which the reciprocating cross beams 36 are mounted and which is movably supported with respect to the base and thus the static grate plates 30.
  • each conveying means 35 may be driven by a separate actuator.
  • the conveying means 35 may be grouped by at least one transmission rod 22 (and/or a movable drive frame) and each group may be driven by at least one separate actuator.
  • the connecting rod 20 converts the circular motion of the drive shaft 11 into a linear reciprocating movement of the corresponding reciprocating conveying means 35.
  • the actuator i.e. the motor 10, the optional reduction gear which is here included in the motor 10 and the crank arm 15 are positioned below the clinker inlet distribution system 5.
  • the actuator is easily accessible for maintenance and the length of the connection rod 20 may be augmented.
  • the vertical components of the force for driving the crank arm that has to be compensated by the frame is reduced.
  • the motor could be displaced, but the crank arm should be positioned as far as possible from the pivot 19, to thereby obtain small pivot angles of the connection rod 20 .
  • the electric motor 10 is controlled by a controller 100.
  • the controller 100 controls the rotational speed of the crank arm 15 as function of its angular position, which may be measured by a corresponding sensor.
  • the sensor is preferably integrated in the motor, a motor housing, a gear and/or a gear housing, to thereby protect the sensor.
  • at least one sensor may be installed to determine the actual position x(t) of the reciprocating conveying means and to provide it to the controller 100.
  • Relevant for controlling the rotational speed are two factors, the absolute force exerted to the pivots and other bearings and the speed v(t) of the reciprocating conveying means 35.
  • the absolute force is critical at the dead centers of the crank arm 15, as a reversal of the direction of the reciprocating grate elements occurs.
  • Fig. 2 shows a preferred example for mounting an actuator.
  • the actuator comprises a motor 10 with a rotor 101.
  • the rotor 101 drives an input shaft 122 of a reduction gear 12.
  • the rotor 101 is coupled via a worm drive to the input shaft 122.
  • the input shaft 122 is connected via a planetary gear to a drive shaft 11.
  • the drive shaft 11 is coupled to a crank 15, which is coupled via a first piviot 16 to a connection rod 20 as indicated in Fig. 1 .
  • the drive shaft 11 may be connected to at least one further crank 15 and/or at least a second motor 10 as indicated by the dashed line (cf. Fig. 3 ).
  • the gear 12 has a gear housing 121.
  • the gear housing 121 is supported by a vertical beam 51 (cf. Fig. 1 ) of the frame supporting the clinker inlet distribution.
  • the gear could be mounted to a vertical beam 52 supporting the clinker cooler grate.
  • the vertical beam is an I-beam as well referred to as H-beam due to its H-shaped cross section, i.e. a beam with two parallel flanges being connected by a web.
  • Other beams could be used instead.
  • the drive shaft 11 may extend through a hole in the vertical beam 51 and/or may be supported by an optional bearing 14 being connected to the beam 51 as well and enabling rotation of the drive shaft 11.
  • the bearing 14 is a plain bearing with a bushing 141, but roller bearings may be used as well.
  • the gear 12 and the drive shaft bearing 14 may be attached at opposed sides of the beam 51.
  • the gear can be vertically supported by the drive shaft 11.
  • the beam 51 may provide only a torque support to the gear. This enables to easily replace a defective gear by simply removing the gear from the drive shaft and replacing it by 'pushing' a new gear 12 onto the drive shaft 11.
  • the gear may have a separate output shaft being coupled by a releasable coupling to the drive shaft 11 as explained above.
  • the drive shaft 11 is a hollow shaft being form fittingly received by the output shaft's 11 end (or vice versa).
  • the weight of the gear is supported by the drive shaft 11, which in turn is supported by the drive shaft bearing 14.
  • the drive shaft bearing 14 may of course be attached to the same beam as the torque support of the gear 12.
  • Fig. 3 shows two coupled actuators.
  • the actuators are similar to the actuator as explained with respect to Fig. 2 . Accordingly, the same or similar parts have identical reference numerals.
  • the embodiment of Fig. 3 has two motors 10, each being coupled by a gear to a common drive shaft 11.
  • the drive shaft 11 has two cranks 15, oriented in parallel.
  • Each crank 15 is connected via a (first) pivot 16 to a connection rod, which is connected to at least one reciprocating conveying means, e.g. as shown in Fig. 1
  • Fig. 4 is a diagram showing the motor's rotational speed (rpm) on the right ordinate and the absolute value of the speed v(t) of the reciprocating conveying means on the left ordinate.
  • the abscissa is the time axis and T indicates the period T.
  • the diagram shows an example relation for a motor driving a crank drive via a reduction gear as shown e.g. in Fig. 1 to Fig. 3 .
  • the rpm of the motor (dashed line) is reduced to a first constant value ⁇ f,const (at t 1 ). This constant value is maintained until t 2 .
  • FIG. 5 A further example of a movement profile of the reciprocating conveying means 35 is depicted in Fig. 5 .
  • the abscissa is the time axis and the ordinate shows the velocity v(t) of the reciprocating conveying means 35 along the direction indicated by the double headed arrow 3, wherein a positive velocity points away from the kiln 90.
  • a cycle starts with a gently increasing velocity v(t) (t 0 ⁇ t ⁇ t g ) to slightly increase the force to be transmitted by the pivots. Next the velocity increases faster (t g ⁇ t ⁇ t a ).
  • the acceleration may be constant in this section, but preferably the force to be transmitted by the pivots 19 is kept constant.
  • the speed of the reciprocating conveying means 35 may reach a maximum forward speed v f,max , that is reduced when reaching the forward dead center point at t f . Slowing down may be accomplished much faster, as the force transmitted between the crank 15 and the transmission rod 20 simply needs to be reduced, e.g. to zero.
  • the motor idles with a decreasing rotational speed that corresponds to the deceleration of conveying means 35 due to the clinker on top of the grate, friction and the like in case the motor would be decoupled from the respective reciprocating conveying means. Accordingly the pivots 16, 19 are so to speak unloaded during deceleration at least for a period of time during deceleration.
  • the subsequent acceleration in the inverse direction follows the same principle as the acceleration in the forward direction, but the maximum retraction speed v r,max is preferably bigger than the maximum forward speed v f,max .
  • the absolute value of the maximum acceleration in the rearward direction i.e. when retracting the reciprocating conveying means 35, is bigger than the absolute value of the maximum acceleration in the forward direction, i.e. when pushing the reciprocating conveying means 35 forward.
  • the effect is that the transition to slide friction between the retracted conveying means 35 and the clinker residing on top of it takes place quickly.
  • the reciprocating conveying means 35 reaches its rearward dead center, it is slowed down to zero at v(T).
  • the absolute value of the speed reduces at a very high rate, i.e. the absolute value of the deceleration when approaching a dead center is preferably bigger than the absolute value for the acceleration away from said dead center.
EP15180131.3A 2015-08-07 2015-08-07 Zementklinkerkühlrost Active EP3128275B1 (de)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP15180131.3A EP3128275B1 (de) 2015-08-07 2015-08-07 Zementklinkerkühlrost
ES15180131.3T ES2669005T3 (es) 2015-08-07 2015-08-07 Rejilla de enfriamiento de clínker de cemento
DK15180131.3T DK3128275T3 (en) 2015-08-07 2015-08-07 Cement clinker cooling grate

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP15180131.3A EP3128275B1 (de) 2015-08-07 2015-08-07 Zementklinkerkühlrost

Publications (2)

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EP3128275A1 true EP3128275A1 (de) 2017-02-08
EP3128275B1 EP3128275B1 (de) 2018-02-21

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EP (1) EP3128275B1 (de)
DK (1) DK3128275T3 (de)
ES (1) ES2669005T3 (de)

Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE878625C (de) * 1938-10-03 1953-06-05 Mikael Dipl-In Vogel-Jorgensen Vorrichtung zur Behandlung von Schuettgut mit Gas, insbesondere zum Kuehlen von Zementklinkern
DE1841381U (de) 1961-08-22 1961-11-09 Peters Ag Claudius Treppenrostlagerung fuer kuehler, insbesondere klinkerkuehler.
FR1316779A (fr) * 1962-02-22 1963-02-01 California Portland Cement Co Procédé et appareil de commande de four
DE1985673U (de) 1967-12-18 1968-05-22 Polysius Gmbh Vorrichtung zur kuehlung von gebranntem oder gesintertem gut.
DE2346795A1 (de) 1973-09-17 1975-03-20 Polysius Ag Rostkuehler
EP0260432A2 (de) * 1986-09-19 1988-03-23 Krupp Polysius Ag Vorrichtung zum Antrieb eines Schubrostkühlers
EP0718578A2 (de) 1992-12-23 1996-06-26 F.L. Smidth & Co. A/S Verfahren und Kühler zum Kühlen von körnigem Produkt
EP0786637A1 (de) 1996-01-25 1997-07-30 Krupp Polysius Ag Schubrost zur Behandlung von Schüttgut
DE10118440A1 (de) 2001-04-12 2002-10-24 Wedel Karl Von Lageranordnung zur pendelnden Aufhängung des Schwingrahmens eines Förderrostes
DE202006012333U1 (de) 2006-08-10 2007-12-13 Claudius Peters Technologies Gmbh Kühler für Schüttgut mit einer Abdichteinrichtung zwischen benachbarten Förderplanken
DE102006037765A1 (de) 2006-08-11 2008-02-14 Polysius Ag Kühler
CN202485465U (zh) * 2012-03-10 2012-10-10 泰安中意粉体热工研究院 L型竖式冷却装置
US8397654B2 (en) 2009-02-17 2013-03-19 Ikn Gmbh Grate plate arrangement
EP2843342A1 (de) 2013-08-27 2015-03-04 Alite GmbH Klinkerkühler

Patent Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE878625C (de) * 1938-10-03 1953-06-05 Mikael Dipl-In Vogel-Jorgensen Vorrichtung zur Behandlung von Schuettgut mit Gas, insbesondere zum Kuehlen von Zementklinkern
DE1841381U (de) 1961-08-22 1961-11-09 Peters Ag Claudius Treppenrostlagerung fuer kuehler, insbesondere klinkerkuehler.
FR1316779A (fr) * 1962-02-22 1963-02-01 California Portland Cement Co Procédé et appareil de commande de four
DE1985673U (de) 1967-12-18 1968-05-22 Polysius Gmbh Vorrichtung zur kuehlung von gebranntem oder gesintertem gut.
DE2346795A1 (de) 1973-09-17 1975-03-20 Polysius Ag Rostkuehler
EP0260432A2 (de) * 1986-09-19 1988-03-23 Krupp Polysius Ag Vorrichtung zum Antrieb eines Schubrostkühlers
EP0718578A2 (de) 1992-12-23 1996-06-26 F.L. Smidth & Co. A/S Verfahren und Kühler zum Kühlen von körnigem Produkt
EP0786637A1 (de) 1996-01-25 1997-07-30 Krupp Polysius Ag Schubrost zur Behandlung von Schüttgut
DE10118440A1 (de) 2001-04-12 2002-10-24 Wedel Karl Von Lageranordnung zur pendelnden Aufhängung des Schwingrahmens eines Förderrostes
DE202006012333U1 (de) 2006-08-10 2007-12-13 Claudius Peters Technologies Gmbh Kühler für Schüttgut mit einer Abdichteinrichtung zwischen benachbarten Förderplanken
DE102006037765A1 (de) 2006-08-11 2008-02-14 Polysius Ag Kühler
US8397654B2 (en) 2009-02-17 2013-03-19 Ikn Gmbh Grate plate arrangement
CN202485465U (zh) * 2012-03-10 2012-10-10 泰安中意粉体热工研究院 L型竖式冷却装置
EP2843342A1 (de) 2013-08-27 2015-03-04 Alite GmbH Klinkerkühler

Also Published As

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ES2669005T3 (es) 2018-05-23
EP3128275B1 (de) 2018-02-21
DK3128275T3 (en) 2018-05-28

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