DK3128275T3

DK3128275T3 - Cement clinker cooling grate

Info

Publication number: DK3128275T3
Application number: DK15180131.3T
Authority: DK
Inventors: Jörg Hammerich; Martin Deutgen; Peter Hennemann
Original assignee: Alite Gmbh
Priority date: 2015-08-07
Filing date: 2015-08-07
Publication date: 2018-05-28
Also published as: EP3128275B1; EP3128275A1; ES2669005T3

Abstract

A cement clinker cooler grate 1 for cooling and conveying cement clinker in a forward direction 2 comprising a grate surface for supporting the clinker, which is conveyed by some reciprocating conveying means 35, e.g. a reciprocating row of grate plates 35, being arranged one besides of the other on a reciprocating cross beam 36, provides reduced installation, operation and maintenance costs if the actuator for driving the reciprocating conveying means 35 is an electric motor 10 being operably connected to the reciprocating conveying means 35 and if a controller 100 is connected to the electric motor 10 for controlling the rotational speed of the motor 10 as a function of the position and/or the direction of movement of the reciprocating conveying means 35.

Description

DESCRIPTION

Field of the invention [0001] 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.

Description of the related art [0002] In 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. On the grate floor, 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. In addition 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.

[0003] These 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: • Reciprocating conveying means, i.e. a part of the grate and/or separate pushers move forth and back in an essentially linear oscillation, thereby conveying the clinker on top of the grate. The reciprocating movement is thus an oscillation of the reciprocating conveying means, wherein the oscillation may take place at least essentially parallel to the conveying direction and/or the grate surface. Such systems are disclosed e.g. in EP 2 843 342, DE 20 2006 012 333 U1, DE 10 2006 037 765 A1, US 8,397,654, EP 786637 A1 to name only a few. • Drag-chain conveyors, i.e. systems based on conveying means that are moved forward above the grate surface and moved back to the kiln facing side of the grate below the grate. These systems mostly comprise chains to which the conveying means are attached (cf. EP 07 185 78 A2, Fig. 3).

[0004] EP 0 260 432 A2 discloses a drive for a conveyer grate for cooling and conveying, e.g. cement clinker. The drive comprises an electric motor having a rotor being coupled in parallel with the input shafts of two reduction gears. Each reduction gear comprises an output shaft being configured as crank shaft which are each coupled to the same reciprocating frame of the conveyor grate.

[0005] DE 878 625 discloses a cement clinker cooler having a clinker cooler with a conveyer grate for conveying and cooling the clinker. The conveyor grate is inclined to an extent that the clinker just does not slide downwards. Clinker transportation is obtained by reciprocating rods being arranged parallel to the grate surface. The rods are connected to a crank disc being driven by an electric motor. The speed of the reciprocating rods is controlled in response to the height of the clinker bed on the grate. A scanning arm senses a change of the height of the clinker bed and switches resistances in series with the electric motor to thereby slow the motor down or speed it up, depending on the direction of the pivotal movement.

[0006] FR 1 316 779 relates to the manufacture of cement clinker and addresses controlling the kiln temperature in response to the conveying speed of the clinker-raw meal mixture in the kiln. The sintered clinker is unloaded on a grate of a clinker cooler. The clinker cooler comprises a vibration conveyor and secondary air is heated in the clinker cooler thereby cooling the clinker in turn down. The vibrational speed of the conveyor grate is controlled as a function of changes of the pressure of the secondary air.

[0007] CN 202485465U provides an example for a clinker cooler with conveyor grate. • Belt conveyors or chain conveyors, examples are suggested e.g. in DE23 46 795 or DE1 985 673.

Summary of the invention [0008] Here, we focus only on clinker coolers with the reciprocating conveying means. Presently, these reciprocating conveying means are driven by hydraulic cylinders. These enable to reliably and precisely drive the reciprocating conveying means and to provide the required high drive forces, which are depending on the size of the grate, but can easily reach 500kN or more.

[0009] 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.

[0010] Solutions to the problem are described in the independent claims. The dependent claims relate to further improvements of the invention.

[0011] 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. For example, 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. Conveying may occur for example according to the walking floor principle. In an alternative example 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. In the first example, 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. Briefly, 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.

[0012] The cooler comprises at least one actuator being operably connected to at least one reciprocating conveying means for driving the reciprocating conveying means. Different from the prior art grate coolers, 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. Here '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. In this context hydraulic or pneumatic actuators are preferably not considered as a mechanical connection.

[0013] 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.

[0014] 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, as hydraulic lines, aggregates, etc. are completely omitted. Further, 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.

[0015] The above named '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 connecting rod via some force transmitting means, e.g. a drive frame coupling the connecting rod to said at least one reciprocating conveying means or a cross bar supporting the reciprocating conveying means.

[0016] 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.

[0017] For example two or more motors may be connected to a drive shaft. For example 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 connecting rod to at least one reciprocating conveying means. Briefly, 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.

[0018] In any of these examples the mechanical connection is thus a transmission for converting the rotation provided by the motor into a linear movement of the reciprocating conveying means. Preferably the movement is periodically, i.e. o(t) = o(t + T) wherein o(t) is the angular position of the crank arm at a time t and T is the length of the period, or briefly period. 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.

[0019] The sensor can be e.g. a sensor measuring the angular position a 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.

[0020] Preferably, 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.

[0021] Preferably, 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. Of course the connecting rod's inclination changes when the crank rotates, but here the mean inclination shall define the rod's longitudinal axis. In other words, 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 connecting 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. by a static frame supporting the grate. Further, positioning the connecting rod below the chute enables to use a comparatively long connecting rod, further reducing the vertical components of the drive force to only a few percent of the total force provided to the reciprocating conveying means. The connecting 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.

[0022] Accordingly, the distance dpp between the first pivot point and the second pivot point is at least 10 times bigger than the distance dpa between the first pivot's pivot point and the rotational axis of the crank, i.e. dpp> 10dpa or even better dpps 20-dpa, preferably dpp£ 30dpa.or even dpp£ 50-dpa.

[0023] 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 connecting 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.

[0024] For example 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. Thus 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. For example, a beam of the frame may comprise a torque support blocking a rotation of the gear housing in at least one direction. For example 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. In the simplest case, the output shaft is a hollow shaft being form fittingly received by the corresponding end of the drive shaft (or vice versa). Thus, 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.

[0025] In the simplest case, the rotor rotates at a constant rotational speed. In this case 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 hydraulically actuated reciprocating conveying means.

[0026] Preferably, 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. For example, 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. This results in conveying means that are retracted at a faster speed than being pushed forward as the clinker shall 'stick' to the conveying means when pushed forwards and slide over the conveying means when it is retracted. But different to the prior art, there is no need to provide a complex control of flow valves and no wear of such valves for controlling the plunger's movement.

[0027] For example, the controller may be configured to vary the rotational speed of the motor as a function of the angular position a of the crank arm between preferably at least two constant values: a first value 0JftConst defining a first absolute value of a first constant rotational speed of the motor during the forward movement of the reciprocating conveying means and a second value u)rconst 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 Mf,const ωΓ,const is preferably maintained for a significant period of the forward or backward movement, respectively, of the reciprocating conveying means. Mathematically speaking

and/or

wherein a^, ctf^ an 1, ar>2 are each selected angular positions of the crank arm corresponding to a forward movement (indicated by index f) or retraction (indicated by index r) of the reciprocating conveying means between the two dead centers. In the vicinity of the dead centers the corresponding ramp up or ramp down of the rotational speed may take place.

[0028] The rotational speed of the motor u>fiConst during the forward movement of the reciprocating conveying means is preferably smaller than the corresponding rotational speed during retraction u)nconst, i.e. uJfiConst < u)rtConst, more preferred: 1.5 wiconsi < u)riConst, or better: 2 · u)fconst < 0Jr,const or even 3 0Jf const < 0Jrconst. Astonishingly, the force Fr required for retracting the conveying means is essentially constant * °>' uCOf but the force Ff for driving the reciprocating conveying means forward increases with u)f. Thus 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.

[0029] Accordingly, within reasonable limits, (Ofconst can be minimized and corconst can be maximized for a given required conveying speed of the clinker to thereby reduce the mean load of the transmission. In other words, upon a request for augmenting or reducing the clinker conveying speed preferably only ojfconst is augmented or reduced, respectively as 0Jrconst should be kept at least almost constant close to its designed maximum, as it should always be as large as reasonable. Only to define borders, the change in curconSf for change of the conveying speed &u)r>const is preferably smaller than 50% of the corresponding change in M)ftconst when changing the conveying speed, i.e. ^Mr>const - 0.5 ku>fconst, preferably &ωΓ,const — 0.25 &(x)f const or even better Δω/-;const - 0·1 ' Δω/;const- [0030] Further, 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 Ms. This preselected value can be e.g. 150% of the torque value Mf,max or Mr,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., Ms<1.5 Mf,max or Ms<1.5 Mr,max, Ms<Mf,max or Ms<Mr,maXj preferably Ms<0.8Mf,max or Ms<0.8Mr,max or even smaller. When passing the dead centers, 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.

[0031] As well, 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 Vf of the reciprocating conveying means to a maximum value Vf>max and to maintain this maximum value Vf>max until the reciprocating conveying means is to be slowed down ('ramp down') prior to retracting the respective reciprocating conveying means. Thus here, the motor's rotational speed is controlled to compensate for a nonlinear transmission. In the above example of the crank drive, the controller may thus compensate the sinusoidal relationship between the speed of the conveying means and the crank arm's angular position.

[0032] 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.

[0033] The ramp down of the at least one conveying means' forward speed is preferably steeper than the ramp up of the forward speed. Here '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.

[0034] Retraction of the conveying means may be controlled by the controller in a similar manner. However, the absolute value of the maximum retraction speed vrmax is preferably higher than the absolute value of maximum forward speed Vfmax, e.g. 1.5 vf max<vrimax even more preferred 2 vf max<vrmax or even 3 vf max<vrmax. Further, the relative amount of time during retraction where vr max is maintained is preferably smaller that the relative amount of time where Vf>max is maintained, i.e. tnmax/tntotal < tf,max/tf,total· wherein the trimax is the absolute time where the vnmax is maintained, tr,total is the duration for retracting of the reciprocating conveying means, tfimax is the absolute time where the Vf max is maintained and tf,total is the duration of the forward movement. Neglecting eventual waiting times at the dead centers, the period T of a complete cycle is T = ttotar tf,total + V,total- ln step grate coolers the waiting time is preferably very small (zero or close to zero). In walking floor concepts, the waiting time makes a significant portion of a complete period, i.e. T =tfjt0tai + tr,total + U where tj is the delay (waiting time).

[0035] This can be realized very efficiently by controlling the crank's angular speed as a function of its angular position. For example 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. As already explained above, said electric motor may have a rotor being coupled via at least a crank and a connecting rod to the least one reciprocating conveying means. Of course there may be pivots connecting the crank and the connecting rod and the connecting rod and the conveying means as explained above. The rotational speed of the motor may be controlled to linearize the movement of the conveying means. For example, the rotational speed may be controlled as a function of the crank's spatial orientation, i.e. its angular position. In a preferred embodiment the motor is coupled via a reduction gear to a drive shaft. The drive shaft drives and optionally supports the crank.

[0036] In a particularly preferred example, a sinusoidal movement of the crank in the direction of the reciprocating movement is compensated at least partially. The displacement of the pivot point or pivot axis (briefly simply 'pivot point') in the reciprocating direction of the reciprocating conveying means is sinusoidal, i.e. when orthogonally projecting the pivot point connecting the crank and the connecting rod onto a plane which is parallel to the direction of the reciprocating movement, the displacement Δχ(α) in the x direction which is supposed to be the direction of the reciprocating movement of the reciprocating conveying means, is sinusoidal, i.e. Ax(o)=l cos(a), wherein a is the angle of the crank arm and I the length of the crank arm. Accordingly, the velocity of reciprocating conveying means can be set by defining

thus it is possible to maintain a constant velocity

of movement of the reciprocating conveying means by adjusting the angular velocity α(α). Of course this is possible only for those angles a, where 1/sin(a) does not diverge, which is at the dead centers. Thus, between the dead centers, the velocity of the reciprocating conveying means can be adjusted to almost any reasonable value. 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.

[0037] Preferably, the absolute value of the slope of the velocity v(t) (i.e.

) of the reciprocating conveying means has at least a local minimum when the velocity v(t) changes its sign.

[0038] Further, as explained above, it is advantageous, if 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.

[0039] Although not always explicitly stated, all of the above explained examples for the movement of the reciprocating conveying means and the motor's rotational speed may be controlled by the controller. Further, the optional reduction from the motor's rpm to the drive shaft rpm is supposed to be fixed, thus

wherein c is a constant. Controlling the motor's rotational speed thus is equivalent to controlling the crank's rotational speed and thus its angular position.

Description of Drawings [0040] In the following the invention will be described by way of example, without limitation of the general inventive concept, on examples of embodiment with reference to the drawings.

Figure 1 is a schematic side view of a partially assembled cooling section of a cement clinker line,

Figure 2 shows a cross section of an actuator unit,

Figure 3 shows a cross section of a further actuator unit,

Figure 4 shows a velocity profile of reciprocating conveying means, and Figure 5 shows a further velocity profile of reciprocating conveying means.

[0041] In Figure 1 a preferred embodiment according to the invention is shown: Cement clinker may be unloaded from a kiln 90 onto a clinker inlet distribution system 5. In this example, 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. Preferably, 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'.

[0042] This grate 1 comprises grate plates 30, 35 on cross beams 31, 36. Typically 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. In this example 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. Only to ease understanding, 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. When pushing the movable grate plates 35 forwards, the clinker is pushed in the forward direction 2. Subsequently, 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.

[0043] 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.

[0044] 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 connecting rod 20. The at least one connecting rod 20 is attached as well to a reciprocating conveying means 35. In this example the reciprocating conveying means 35 is connected to the connecting 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. Alternatively, each conveying means 35 may be driven by a separate actuator. As further alternative 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. In any case, when the motor 10 drives the crank arm 15, 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.

[0045] As can be seen, 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. Thereby, the actuator is easily accessible for maintenance and the length of the connecting rod 20 may be augmented. Thereby, 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 connecting rod 20 .

[0046] 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. Alternatively 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.

[0047] 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. Here, but only as example, 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 connecting 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. Alternatively, the gear could be mounted to a vertical beam 52 supporting the clinker cooler grate. In this example, 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. As shown, 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. In this example the bearing 14 is a plain bearing with a bushing 141, but roller bearings may be used as well. As shown here, the gear 12 and the drive shaft bearing 14 may be attached at opposed sides of the beam 51. Alternatively, 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. In this case the gear may have a separate output shaft being coupled by a releasable coupling to the drive shaft 11 as explained above. For example, the drive shaft 11 is a hollow shaft being form fittingly received by the output shaft's 11 end (or vice versa). This enables to simply remove the gear in case of failure and to literally push a new one on the drive shaft 11. 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.

[0048] 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 connecting rod, which is connected to at least one reciprocating conveying means, e.g. as shown in Fig. 1 [0049] 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. At to=0 the rpm of the motor (dashed line) is reduced to a first constant value cOfyConst (at t-ι). This constant value is maintained until t2- At t2 the crank reaches its dead center, and the rotational speed is maximized to reach a second constant value u>riConst at t3 which is maintained as long as the reciprocating conveying means is retracted, i.e. until the end of the period T. The solid line indicates the corresponding speed of the reciprocating conveying means. As can be seen, between t-| and t2 as well as between t3 and T, i.e. when the rotational speed ω(ί) is constant, the speed v(t) is sinusoidal. Further, as coriConst> 00frConst the retraction time T-t2 is shorter than the time of the forward movement t2-to- [0050] 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) (t0<t<tg) to slightly increase the force to be transmitted by the pivots. Next the velocity increases faster (tg<t<ta). For example, 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 Vf max, that is reduced when reaching the forward dead center point at tf. 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. In this case 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 vrimax is preferably bigger than the maximum forward speed Vf>max. Preferably, 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. When the reciprocating conveying means 35 reaches its rearward dead center, it is slowed down to zero at v(T). At t=T the cycle may start again, i.e. v(t)=v(t+T). In some embodiments the cycle may restart after a delay td- As can be seen from the Figure, when approaching a dead center, 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.

[0051] The invention was explained above with respect to a step grate cooler, but the transmission of the rotation of a motor driving the drive shaft and the considerations with respect to the velocity profile of the reciprocating conveying means can be transferred as well to grates of planks being arranged one besides of the other in parallel to the conveying direction, wherein at least some of said planks are movably supported to enable a reciprocating movement of said planks. These movable planks can be driven by a similar or the same transmission (electric motor, optional reduction gear, crank and connecting rod) as explained above and thus become reciprocating conveying means. Dimensioning has to be adapted, of course. The controller and the methods for controlling the motor(s) can be used as well.

List of reference numerals [0052] 1 cement clinker cooler grate, briefly 'grate' 2 conveying direction / forward direction 3 double headed arrow indicating reciprocating movement 4 grate surface 5 clinker distribution system 6 side wall 9 base 10 electric motor (with optional reduction gear) 11 drive shaft 12 gear / reduction gear 14 drive shaft bearing 15 crank / crank arm 16 pivot 19 pivot 20 connecting rod 22 transmission rod 30 grate plates 31 cross bars (static) 35 movably supported grate plates / reciprocating conveying means 36 cross bars (reciprocating, movably supported) 37 guide rails 39 cooling slits 50 grate plates 51 vertical beam 52 vertical beam 55 cross beams 57 girder 59 cooling slits 90 kiln 100 controller 101 rotor 121 gear housing 122 input shaft 123 gear wheel 124 gearwheel (e.g. sun gear) 125 gearwheel (e.g. planetary gear) 126 gear wheel (e.g. gear ring) 141 bushing of drive shaft bearing 151 pivot axle

REFERENCES CITED IN THE DESCRIPTION

This list of references cited by the applicant is for the reader's convenience only. It does not form part of the European patent document. Even though great care has been taken in compiling the references, errors or omissions cannot be excluded and the EPO disclaims all liability in this regard.

Patent documents cited in the description • EP2843342A j~00031 • DE2020Q6Q12333U1 f00031 • DE102006037765A1 [0003] • US8397654B [06031 • EP786S37A1 |Ό003| • ΕΡ0718578Α2Γ60031 • ΕΡ0260432Α2Γ00041 • DE878625 Γ00051 • FR1316779 Γ00061 • CN202485465U |000?1 • DE2348795 Γ06871 • DE1985673 ίΟΟΟΤΙ • DE10118440 Γ60421 • DE1841381 Γ00421

Claims

A cement clinker grate (1) for cooling and conveying clinkers in a forward direction, comprising at least: - a grating surface (4) to support the clinkers, - at least one reciprocating feed member (35), - an actuator which is operatively connected to the reciprocating feeder (35) to drive the reciprocating feeder (35), the actuator comprising at least one electric motor (10) operatively connected to the reciprocating feeder (35) to drive the feeder (35) , characterized in that the actuator further comprises a control (100) connected to the electric motor (10) for controlling the rotational speed of the motor (10) as a function of the position and / or the direction of movement of the reciprocating feeder (35).

Cement tile cooling grid (1) according to claim 1, characterized in that the motor drives at least one crank (15), to which a connecting rod (20) is connected via at least a first hinge joint (16), which connecting rod (20) is connected to said reciprocating feed member (35) or a support thereof, via at least one other hinge member (19).

Cement tile cooling grid (1) according to claim 2, characterized in that the hinge link (16) of the connecting rod (20) is located below a clinker inlet distribution system (5) or in extension of the clinker inlet distribution system (5) and the connecting rod (20) extends within it. ± 30 °, at least approximately parallel to the feed direction (2).

Cement tile cooling grid according to claim 2 or 3, characterized in that the distance dpp between the hinge points of the first and second hinge joints (16, 19) is at least 10 times greater than the distance dpa between the hinge point of the first hinge joint (16) and the axis of rotation of the the crank (15), i.e. dpp> 10 dpa-

Cement tile cooling grid (1) according to any one of the preceding claims, characterized in that the grating (1) providing the grating surface (4) is supported on a base (9) via a frame (37, 51, 52, 55) below the grating (1) and the electric motor (10) being connected to said frame (37, 51, 52, 55).

Cement tile cooling grid (1) according to any one of the preceding claims, characterized in that the rotational speed of the motor (10) is lower by movement of the reciprocating feeder (35) in the forward direction (2) than by retraction thereof.

Cement clinker grate (1) according to any one of the preceding claims, characterized in that the cement clinker grate (1) comprises at least two reciprocating conveying means (35) which are connected to each other via at least one transmission rod (22) connecting at least two reciprocating feed means (35) at a constant distance.

Cement clinker cooling grid (1) according to claim 7, characterized in that the transmission rod (22) is integrated in a movable drive frame.

Cement tile cooling grid (1) according to any one of claims 1 to 8, characterized in that the actuator comprises a drive shaft (11) with at least two cranks (15), each connected via a connecting passage (20) to at least one reciprocating feeder (35).

Cement clinker chiller (1) according to any one of claims 1 to 9, characterized in that at least one electric motor (10) is connected to the drive shaft (11) via at least one reduction gear (12).

Cement tile cooling grid (1) according to any one of claims 1 to 10, characterized in that the motor (10) and / or gear (12) and / or a bearing (14) for the crank (15) is supported by at least one vertical beam (51.52) which supports a rice floor in the tile cooler and / or a tile inlet distribution system.

A method for controlling the velocity v (t) of at least one reciprocating feeder (35) in a cement clinker chiller (1), comprising at least movement of the reciprocating feeder (35) by operating an electric motor (10), wherein the reciprocating drive means (35) is connected to the motor (10) at least via a crank arm (15) and a connecting rod (20) for linearizing the rotational movement of the motor, characterized in that it further comprises controlling the rotational speed of the motor (10). as a function of the angular position of the arm of the crank (15).

Method according to claim 12, characterized in that a sinusoidal movement of the crank (15) in the direction of the reciprocating movement (3) is compensated by the control (10) providing a velocity profile of the reciprocating feeding means (35) having in the at least one section where a velocity different from zero is constant and / or the rotational speed of the motor is varied as a function of the angular position α of the arm of the crank between at least two constant values (ωη max, 10f, max) -

Method according to claim 12 or 13, characterized in that the absolute value of the slope of the velocity v (t) has at least one local minimum when the velocity v (t) changes its sign.

Method according to any of claims 12 to 14, characterized in that the maximum angular velocity of the crank (15), with retraction of the at least one reciprocating feeder (35), is greater than the maximum angular velocity of the crank (15), during forward pushing of the at least one reciprocating feeder (35).