DE1954146A1 - Loading device for aggregates present in the form of bulk goods - Google Patents

Description

PATENT ADVOCATE DlPL -ING. K. BUNK

8 monks 6/27 ΟΚΤ.

Jrogerstraije 4 / y

«54146

Loading device for present in the form of bulk material Surcharge open.

The present invention relates to loading before direction for the form of aggregates present in bulk «

The loading device - to the present invention relates, has the task of providing a bulk material usually to pick up additive material deposited on the ground as a pile and to supply the consumer parts, which can be another transport device, a container, etc.

Such loading devices consist of one location fixed holder in which a rotational axis (vetical or subvertical or possibly slightly inclined) is, taa welohe «rotates in a projecting frame or era,

which, in cooperation with other active organs, creates a trans Port device forms, the frame or the arm during the loading activity one depending on the respective FaIX describes a fluctuating circular arc, which, however, can be of any width and is often 180 ° and more.

The 'transport device acts on the at every moment

W through the axis of rotation vertical plane and takes on aggregates, which it transports in the radial direction towards the axis and usually, if necessary, lifts to feed them to the desired location,

The active organs of the Tmasport device germinate from beli £ Be biger execution and be available, for example, from a chain, which carries cup and is in a closed Circle moves under the action of drive organs »Be i ^ For example, the transport organs can conventionally »cups

k conveyor, one or more screws or one or more Ligaments or a combination of such organs. It can other transport organs are also provided, which enables are to pick up the aggregate material and convey it radially and, if necessary, also vertically.

The rotary movement around the fixed axis of the vorsprin lowering frame or arm is rewarded as a "pivoting movement", which word in this · * context in the. following B «» chrei> Exercise is used «Ss is borrowed from view that dm Transport! organ «in · drive source · xugeornet his nut, soft«

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is an electric motor or which can also be hydraulic or pneumatic.

The pivoting movement could be generated manually at however, it occurs to the more sophisticated devices mechanically, at least in the active phase and often also in the return phase, if the projecting one Frame of the transport conveyor as soon as it is at the end of its Pivoting movement arrived and the loading of the aggregates berfdet is, returns to its starting position, by one carry out further work cycle »

The mechanical implementation of the pivoting movement during the active phase without direct human control, i.e. the automatic pivoting, brings different Problems with themselves, which are mostly caused by measures described in applicant's other patents have been drawn. In these patents there is a movement system. described for the swivel arm, in which a continuous and controlled, in particular constant, thrust is applied against the material to be loaded.

This thrust is converted into a moment that is applied to the swivel arm by a suitable drive element,

Xn are the applicant's aforementioned patents Organs defined which are involved, the swivel arm a constant moment and a constant thrust, which are constant, at least in the sense that theirs Pivots in narrow and predetermined areas are included.

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A strictly constant thrust can be achieved with extremely simple Devices are generated, such as with a counterweight or with more complicated devices, such as electromagnetic clutches,

On the other hand, to get a boost, if it does is not rigorously constant, by Einreeelun ^ within predetermined and is extremely narrow, and therefore practical

ft can be regarded as constant, so hydraulic Vorrischtungen to aid one can take neispiels way be ± games as those which, which is discussed in more detail later, the object of the patent no. 733 ^ 83 form of the applicant.

When in these devices the thrust fluctuates tends to grow, for example, because the pile of surcharge · » substances due to the different consistency in its different parts or due to a slide motion attributable or from another Reason at a certain point of the pivoting movement of the arm

P of the transport sponsor a greater resistance to jp * · sets, the initial increase in thrust produces a change in the pivoting movement, in practice a slowdown or a standstill, or it is even reduced to a limited extent, so that the predetermined Thrust conditions which are considered to be optimal and which are adjusted on a case-by-case basis by means of suitable settings are changeable, restored.

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It is obvious that this control takes place entirely inside the mechanical complex which effects the pivoting movement and which is referred to in the following for the sake of simplicity as "angular movement unit" or, more simply, "movement unit ¹¹ ".

The changeable, which in the functioning of the Participate in the movement aggregate - recorded; Power, thrust and angular velocity »are by a quantitative Relationship bound "

Assuming that at a certain moment these variables have values that are considered optimal It is obvious that these values cannot be can be maintained unchanged if the working conditions and in particular those of the material to be loaded opposite resistance fluctuate ^.

The fluctuations in these values can be up to one indicated point by a control system inside the movement unit to be controlled"

This system can be such that there is a of these three variables, holding essentially constant, Xn of the above-mentioned patent is essentially the one constant kept variable the thrust,

Similar considerations can be made in connection with the complex of organs which operate the transport conveyor «ad wekche are generally referred to as" transport organs ¹¹ ,

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If, for the sake of understanding, one assumes that the conveyor is a bucket elevator, so are the variables that determine its functioning and which are quantitatively bound, the absorbed force, the displacement speed of the buckets and the tension of the chain carrying the buckets "

The feed speed of the cups is controlled by the amount of loaded material is determined and it is often useful if this is kept constant »

The tension of the chain changes into a point data on the swivel frame or swivel arm, which must not exceed certain values «Venn Be ·» Damage to the device should be avoided.

The one recorded in relation to the built-in motors Force determines the greater or lesser utilization of these organs, for example the electric motor used γ

It is therefore also a for the transport unit. inner. Control system conceivable "

Know this internal rule system continuously work or may be limited to absorbing the fluctuations within predetermined limits,

Bs was ta. **, found that no regulation of the Movement unit or dee transport unit offers the possibility of the optimal operating conditions of the to keep the entire loading device known.

Indeed it is through the consistency and behavior

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the aggregates a relation between the operating conditions of the two aggregates introduced, which from one place to another and from one moment to the other Can fluctuate.

So if the loading device has a duty cycle under optimal operating conditions of the two Aggregate begins and when it then hits more compact material at a certain moment, so change siqh the operating conditions · Venn the movement unit is designed in such a way that the thrust exerted on the swivel arm is kept constant, so the case occurs that the transport conveyor is no longer working at full capacity and that in the case of a bucket conveyor the Do not load the cup sufficiently and therefore the transport unit is poorly used.

If, however, the pivoting transport conveyor encounters less compact material, although it is widely assumed that the applied thrust is due to the Regulation of the movement unit is kept constant, the transport conveyor works above the intended optimal operation, whereby in the case of a bucket conveyor the cups fill up to the predetermined extent and4ls As a result, the transport unit is overloaded and Abnormal mechanical loads on the swivel arm and on the other organs of the transport conveyor occur.

These are examples which, however, do not reflect the fluctuations that can occur under working conditions

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exhaust. Suffice it to say that a change in the consistency, behavior or arrangement of the aggregate to be loaded in a negative sense, the working method influences the mechanical units of the loading device and they are outside the predetermined optimum Conditions misplaced, which sometimes leads to serious inadequacies and can also lead to fractures,

According to the invention, the functioning of the loading device in its complex is always sufficiently close to keep the optimal conditions, and in any case numerous deficiencies are eliminated by a "Locking" between the sports unit and the movement unit is created.

The meaning of the term "lock" is clarified in the ^F olge.

One of the two aggregates is taken into account, Based on optimal operating conditions or in any case on conditions which the predetermined correspond, it is believed that at some point the consistency of the pile of aggregates varies. There is therefore a tendency for the variable quantities which the current mode of operation to fluctuate to fluctuate of the aggregate under consideration,

According to the invention is used one of these great as a control, d _e h ,, their fluctuations are utilized to obtain a signal which via a suitable

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Processing system a change in one or more Size which affect the functioning of the other Print out aggregates and which are therefore classified as "modulated" Large or large can be designated, with this measure between the two units is an optimal one Operating relationship is restored. For example, changing one of the sizes, which express the functionality of an aggregate, a signal generate, which is used to change the operating conditions of the other unit in such a way that the fluctuation caused by the signal itself, is canceled,

In this case, the result of the regulation is the Maintaining a constant value of a certain, as Control variable used variable by locking of the two units,

Since with each unit one also works outside the both variables, which express the mode of operation, can act, since the third is determined by it, one can in the case in which the regulation is based on the same Variable, which serves as a control, acts, a other variables of the same aggregate "independent control,. and, for example, within reading limits or even keep it constant "

Because according to maxi gem & ee a special form of execution According to the invention, the speed of movement of the transport conveyor, in the case of a bucket conveyor *

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the displacement speed of the cups and in the case of a Worm the angular speed of its axis, constant keep"

This speed is therefore determined by the lock-up ratio of the two aggregates excluded. As a control variable the power consumed by the motor of the transport unit can be used »

If the consistency of the aggregate varies in such a way that to keep the predetermined pushing speed constant, the cup with the current value of the push on the swivel arm, which prevails at that moment, is necessary to increase the power consumed by the motor of the transport unit, then this can increasing tendency is selected as ignal for changing the Schubesn the ^ n this case as a modulated variable, serving, so that it is performed the whole system in sMbhe operating conditions that the TransportftKlerer with the same predetermined Versohubgeschilindigkeit the cup and with the same absorbed by the motor power working _s can wherein consequently the change in the gross "used as control is canceled,

According to a preferred embodiment of the invention the locking of the units is pressed in the constant » withstand all operating conditions of a unit, preferably the transport conveyor, $ edooh does not have to necessarily the case «For example, in the

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Above in amount drawn case in which the controls size, which is the power consumed by the transport unit, the regulation takes place in such a way that the thrust on the swivel arm is varied, but not to such an extent, that the fluctuations in performance are completely eliminated, so that a certain increase in the power consumed can take place, which is kept within predetermined limits.

, You could also similarly the thrust on the swivel arm and the speed of movement of the conveyor or change the thrust and the angular speed of the swivel arm at the same time.

For the practice of the invention it is only required that from changing one of the those Functioning of one of the units that print out large quantities picked up signal changes in at least one which expresses the functions of the other Express the aggregate · This realizes the aforementioned interlocking of the two aggregates.

The invention includes the presence of a processing system », which at the input of one of the two units of the loading device and at the output of the other unit at. connected to both units and programmed in such a way that the output signal in the second unit works. nelle compensating changes in the fluctuations of the first unit, which caused the input signal

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have generated, for example, but not necessarily, in the sense that the inlet is at zero or at least against Is brought to zero.

For a better understanding of the invention, the general structure of the loading device and an example of a hydraulic thrust constant genes Ratoe is mounted on the swivel arm% of ±? T _t which parts form no subject of the invention, explained in more detail.

Xn of the Drawing Figure 1 shows Pig x schematich device consisting of a bucket elevator, "^ ig. 2 schematically shows a hydraulic generator for generating a constant thrust, which forms the subject of another patent of the applicant, the Flg. 3 and h a loading ^ schematically in elevation and plan view of the elaboration way of the loader with respect to pile of bulk cargo aggregates which Fig. 5 shows schematically a poss inches VerrijB gelungssystem according to a preferably embodiment of the invention by means elektricher circuits, Fig. 6 schematically shows an according with respect to that schema Figure " 5 perfected scheme, FIG. 7 schematically the thrust generator according to FIG. 2, which has been adapted and modified according to the improvements according to the present invention, FIG. 8 a variant of the instantaneous overpressure valve provided in the diagram according to FIGS. 7-9-11-12 is, Fig «9 schematically a thrust generator assigned to the outside of the traction unit and a pump with änderlicher before "power used ^F ig · 10 the pump

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variable performance according to Pig «9 which besides the Pulling unit also automatically pulls the thrust unit », is orderly, Fig. 11: schematically consisting of a complex consisting of a traction unit - a thrust generator, which is operated entirely by means of a hydraulic circuit and with a single dummy is realized, which by means of a flow divider feeds both the traction motor and the thrust unit, and Fig. 12 schematically shows a complex consisting of a pulling unit - Thrust generator implemented entirely by means of a hydraulic circuit, but with two pumps is,

G * mäsa of Fig. 1 is the loading device shown provided with a bucket elevator. The stationary holder, generally designated 10, consists of a row of interconnected 'parts which form part of the legs of a silo 11 or with. be connected to this can. The swaying frame, generally designated 12 or swivel arm, which consists of a lattice structure, is dash-dotted on the frame 10 for the purpose of rotating it about one indicated and denoted by the reference number 19 Articulated vertical axis formed by bolts 17 and 18 which is mounted on the parts 16 and 15 of the frame 10 are. The 1% movement unit is mounted on the frame 10, which creates the movement that serves it; the pivot arm 12 to drttckan against the pile of aggregates and cause the angular movement of the arm, *

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On the swivel frame or swivel arm 12 rollers 13 are mounted, which support the chain 20 »The buckets 21 are attached to the chain 20, which preferably consist of a supporting base 22, with which they are anchored to the chain, and a bucket 23 exist with two openings, which is used to take up the aggregate material. This type of cups is known per se and forms the subject of patent specification nos. & 73 366 and 8Z1 750 of the applicant,

In the contact zone with the aggregates, the cups run in the direction indicated by the arrow Zk in FIG. The material falls onto a chute 25 and is then 'conveyed' to where it is needed.

On the swivel frame 12, the transport unit is mounted, which actuates the drive rollers 26 (in the drawing, the axis of the unit 27 is perpendicular to the Axis of the letter 26 shown, but it could also others lie).

According to a preferred embodiment, the transport unit has Embodiment of the invention «a motor and» a hydraulic one Sohubgenerator (or movement generator) on the in Fig. 2 .Is shown. This generator forms the. Subject of the applicant's patent no. 733 483 to which reference is made in this context. For better

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However, understanding of the present invention will be a brief one Description of construction and functionality given.

The hydraulic thrust generator, shown generally at 30 primarily has a pump 31 which, according to FIG Drawing of a gear pump that produces a liquid usually oil, in one of the two sections, in the right or left, of the generator, depending on the direction of movement of the swivel arm in one or the other direction, i.e. clockwise or counterclockwise, promoted. The movement is reversed by reversing the Rotation of the motor, not shown in the drawing, which actuates the pump 31,

Under the operating conditions described here, the liquid is fed into the right-hand section of the generator. promotes and the rotation of the element connected to the pivot arm, which is the shovel 36, takes place when viewed the drawing figure counter-clockwise,

The pump 31 consequently pushes the 01 into the channel 32. ON its way, the oil first encounters a pressure relief valve 33, which opens when the pressure exceeds a certain limit value and enables the oil to return to the pump 31 in a short circuit, Xn der sequence meets the egg on a non-return valve 3 ^, and then enters the chamber 35 'in, in which prints it against the blade 36, the ^AU due to the different pressure between the chamber 35 and the chamber 37 ^ aer other side of the blade prevails, counterclockwise, at

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Viewing the drawing figure, is shifted, whereby the chamber 37 becomes smaller and smaller.

The back pressure in the chamber 37 can be a certain Limit value due to the presence of the back pressure relief valve 38, which is switched on on the path 32 * of the oil in the left side of the pump, must not be exceeded. At 39, an oil container is provided which, thanks to the piston 4o, can also be used for filling during operation of the unit can be opened and serves to keep the amount of oil required at that point (in the circuit) constant.

If builds up at a point a sudden resistance to the Vejfschwenkbewegung or if the oscillating conveyor is pushed back by a Erdsturz, 35 ei * ¹ greater pressure builds up in the chamber than the intended pressure on because the sudden resistance and in the chamber 37 add up the prevailing back pressure. The oil flowing through a line 41 now acts on a small piston 42, which is pushed back and allows the oil to flow through a line 43 and enter the chamber 37. The line 44 serves as a vent for the movement of the piston 42, the oil thus tends ^to increase the pressure in the chamber 37 and the excess oil returns to the pump 31 via the valve 38. In this way it is avoided that the thrust exceeds a value that is determined by the setting of valve 4.2 (and the corresponding

Valve 42 * on the other of the device)

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If the oil circuit is reversed, the pressure difference is there between the chambers 37, 35 also reverses and the blade 36 receives a violent thrust that, there the limiter 42 * comes into action, then weakened will. This limiter is pushed back and the oil hits from the line 44 *, but this exit occurs quite slowly, which is why it takes a certain amount of time before the VentiX 42 * has moved back so far that the Leitunh 43 * is opened and consequently a regulation of the Pressure in the chamber 37 takes place * The violent thrust which builds up in this period of time, places the cup over the pin 45 'which is attached to the swivel frame. conveyor from the aggregate heap and interrupts loading.

As you can see, the purpose of this device is a regulation of the movement units, whereby it is avoided that changes in the working conditions are undesirable Cause changes in the thrust of the swivel arm «

However, as has been stated, the changes in the conditions of the behavior of the accumulation of aggregates to be loaded have! effects on the puncture mode of both the movement unit and the transport unit »

This is illustrated, for example, in FIG. 3, which shows a bucket conveyor seen from the rear, which acts on the accumulation of additives 51. The cups 21 which are attached to the base of the agglomeration of aggregates 50

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take hold, sooner or later cause “instability” Situation of the accumulation itself, since the natural cone of friction has been altered. A small avalanche then falls

in the direction of the loading conveyor, its cup on a There is greater resistance to their displacement, which resistance is due to the double trapezoidal structure of the Cup to a drawer, perpendicular to the axis of the stationary Holder of the loading device gives rise to. This thrust turns into a moment in relation to axis 19} which one, if it is bigger than that «, which one for example is applied by the generator described in ig, 3, a swiveling back of the swivel arm causes until the Balance between the two moments is restored.

Xn of FIG, h one sees the same Seiadevorrichtung with bucket elevators that is associated with a SIl * 1t, in plan view} Matching Caps, with two clusters of aggregates 50 and L 50 · on the sides, Xn cheating this case, the effect of Si portion of the loading about 180 ° »

The following, non-restrictive exemplary embodiments, which relate to further improvements and which can be modified and varied in many respects, without thereby going beyond the scope of the invention, serve to provide a more detailed explanation of the invention. For example, the ^T can ransportaggregat the loading beliiblge a power source such as an electric motor (see unit 27, page ί), a hydraulic motor or

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have a pneumatic motor "

The exemplary embodiments relate to the electrical and hydraulic systems, although there are analogies between the latter and the pneumatic system, that what is said in connection with one is also valid for the other system.

The improvements proposed by the present invention essentially concern loading devices which a3Ls control variable apply the force, which the Transport and pulling unit of the chain system is exposed, whereas the assigned size of the unit of the same name exerted thrust.

It is known that the electric motors and the hydraulic motors are self-regulating, i.e. that they are automatic find the balance of factors which are responsible for its functioning in terms of torque or moment which on their shaft, that is, at the exit, to work together " The form and the way in which they achieve this equilibrium are determined by the structural features, which are known per se to the person skilled in the art and whose further explanation therefore appears superfluous.

As a result, since the motors are self-regulating, with the exception of special work requirements that the SöhwenkfÄrderern knew about, for normal work for which the loading devices are used, no advantage. if the pulling unit is used as a function of the swivel

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unit regulates »Since the traction unit according to a maximum Working standard is designed is dimensioned in such a way that there is a maximum hourly volume of aggregate * moving can and since it is useful for the economy of the system if the loading device always working at its maximum power in order to shorten working hours, it is evident that the constant die

P Use of the pulling unit and the variant the swivel unit is.

The hourly maximum amount of aggregates to be loaded is characterized by the following factors! Displacement speed of the receiving cups (or rotation speed in the case of Schneckerodgl,) Number of cups per unit of length (or thread of the snails and the collecting spirals)

Holding volume of each individual cup (or diameter of the screws or dimensions of the spirals or the like)

^ It is evident that these three factors contribute to the

Working together to meet the maximum hourly output, which performance varies from aggregate to aggregate with the same parameters.

Since the bucket conveyor or any other conveyor is supported by a structure, this is for designed a certain standard load, which standard the maximum hourly output that can be realized by the loading device corresponds to the economic

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Factors on which the invention is based are compatible.

There is consequently one for the loading device optimal conditions of use, which one based on the the device's own limitations, such as construction, built-in power source, economic expediency of Change in these factors, can no longer go beyond

If the parameters are formed by the displacement speed, the number of cups per unit length and the volume of each individual cup as fixed assumes (the parameters of the sponsors, cited, but it is obvious that this is just the egg » The accuracy of the description is made not every time having to enumerate the properties of all swivel conveyors), so it can be seen that it is necessary to achieve the maximum Performance is advantageous, the required drive torque to be chosen in such a way that it is the same or approximately the same for each tent point of the loading device for moving the cup equal to the maximum that can be delivered with continuity from the drive source used and in a predetermined Deviation lies.

To achieve this, you have to turn the pulling motor into the swivel unit map in a way that he is anxious to map this Maintain a constant balance of maximum utilization.

In the description of the parent patent, various technical solutions were announced, such as u, _at

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also those which mainly relate to the locking of the S4fcrenkaggre gate with the pulling unit and are shown in the accompanying drawing figures h and 5. . '.

The strength in ^F. 5, the reference numeral 60 denotes as a conveyor unit a unit which is driven by an electric motor, which is why the value assumed there is the current consumed by the motor in

W is amps. In contrast, the movement unit, not shown in the drawing, comprises an electric motor and an oil-pressure visual lift generator 30, for example of the type shown in FIG Moment by adjusting the two valves k2 and k2 *. determined, whereby the valves 33 - 33 * are set for the maximum value «

In the drawing figure 5 these valves 42 and 42 ·

k shown schematically, whereas the remaining parts of the movement unit, omitted to avoid unnecessary repetitions

According to Flg. 5 is from a stream reader 61 the stream recording of the motor 60 determined · The determined in this way © Signal comes from an electrical circuit the following schemes processed

The primary winding of a »TraneforaaatoP» 6Z is fed from line 77. If you look from the top (when looking at.

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as

the drawing figure) of the secondary winding of the transformer 62 starts, one can reach the lower Sride two partially coincident paths "A path is formed through the pipe 6k at the side of the resistance of the first potentiometer 63 which the movable contact 65 to the conductor 66, from Conductor 66 leads to coil 67 and to conductor 68 in the inside of the resistor of potentiometer 69, which leads from said conductor 68 to floating contact 78 and to conductor? 0.

The other path is formed by the conductor 6k on that side of the resistance of the potentiometer 63, which leads from the movable contact 6 $ to the conductor 7I and from this via the coil 67 to the conductor 72 that side of the resistance of the potentiometer 69, which leads from the conductor 72 leads to movable contact 68 and conductor 70,

If in output split the resistances of these two Circles are identical, the electricity price is balanced and no current flows either in the coil 67 or in the Coil 67

However, if the potentiometer 69, which is for the Nul_L position and the division of the unit is used, is held stationary, the movable contact 65 of the adjusted Potentiometer 63 on a fluctuation in the reading of the amperometer 61, increasing the resistances of the two circles vary in opposite senses and consequently, depending on the case, either coil 67 or coil 67 * is energized while contact 73 is activated by the energized coil

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pulled, closes on one or the other side, whereby the electromagnets 7k and 7 ^ ^{1 are} fed, wass a rotation to the right or to the left of the motor 75 provided with a travel limit.

The rotation of the motor can be used as a modulated signal as a result of the processing of the read signal on the part of the processing circuit described.

On the axis of the motor two eccentrics 76 __, 76 * are attached, which act on the counteracting springs of the valves 42 "'- 42 *, whereby the setting of the thrust generator 30 and consequently the size of the thrust - or the movement which the ^ ewegvongsaggregat the swivel arm is varied.

However, this system is sensitive to sudden pressure fluctuations in the thrust unit and an excessively powerful motor 60 must therefore be used. Moreover, this circuit is unsatisfactory because of its sensitivity to atmospheric influences and to fluctuations in the mains voltage, which fluctuations the circuit interprets as signals from the ammeter 65 and consequently incorporates them into the generation of the modulated signal.

This disadvantage is caused by the presence of the carrier 61, which is connected between the line and the evaluation circuit, is reduced, but not completely switched off.

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6 therefore shows schematically an exemplary embodiment the invention; which is an improvement over that of FIG.

The Fig. 6 schematically shows the motor 80, according to the motor 60 as shown in ^FIGS, 51 and an ammeter 81 in accordance with the amperometer 61 of Fig, 5 "which reads the Stromaufnähme of the motor 80.

However, the signal read is not aiLs directly Input used in the processing or evaluation circuit, but rather an equilibrator S2 to which another signal arrives, which is taken directly from the voltage of the line via a volmeter 83 will.

The equilibrator 82 thus receives two signals, which two different readings correspond to one Current reading 81 and a voltage reading 83, the- • rste Reading represents the actual current consumption of the motor 80, while the other reading is the instantaneous voltage ^ Variation on the power to which the engine is connected in relation to the nominal voltage of the line itself, with the same power output the current consumption inversely proportions! to the tension is.

The equilibrator 82 compares the two signals and generates an output signal by means of known organs, which would take only the variations in the upstream and "alone represents due to the variations on genozanaenen Lei s tung which ^s ignal thus of denScb, wankungön _s

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can be traced back to the Sparmtmgsttn.tersoh.iede determined by the voltmeter 83 are, is liberated.

The signal purified in this way is fed to a Wheatstone * see bridge 8% ^ which is in equilibrium with respect to the given normal conditions. The fluctuations in relation to these normal conditions produce shifts in the Wheats Tone, which are picked up by an electronic amplifier 86 and lead to the continuous generation of a current which is fed to a motor 85 corresponding to the motor 75 of FIG in an analogous way to the valves 42 and ^ 2 * for the setting of the oil pressure thrust generator 30 But the eccentrics 87 and $ 7 * work.

The devices and circuits shown, for example, in FIGS. 5 and 6 can be varied in many respects without going beyond the scope of the invention, since the skilled person numerous other ways and variants to he aiming the same results are known.

It is especially apparent that these devices and circuits can be applied to any type yon swivel conveyors "In fact, the signal which causes the control of the removed conveyor unit controlling the electric motor and hence it is for this purpose unerheclich whether this engine" casters ^ which pull the Bftoherkette »or a worm shaft, or rollers, walah © pull a belt, or a pnetuaa ti see conveyor or any combination of such organs or * drives any conveyor device,""*

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Further it is evident that the circuits and devices which process the read signals and generate the modulated control signals differ from those shown be able to distinguish »The possibility of variation is so great that the description of other examples for the Seems like a skilled person neither necessary nor useful.

As you can see, the two systems described act on the discharge of excess fluid and is the Interlocking or mutual assignment directly proportional to the force required for the control motor of the traction unit,

The following explanations serve for a more detailed explanation. The valves 42 act on the surfaces of the blades (FIG. 3) and in this way produce the pressure difference between them. If, in the case shown in FIG. 2, the chamber 35 is under pressure by actuating the spring controlling the valve kZ while increasing its preload, a greater pressure difference is produced between the end faces of the blade 36 and consequently a greater usable torque on the axis 45 generated. However, this effect is not counteracted by the power of the pump 31, which, since it works constantly, causes a rapid increase in the pressure in the chamber 35 until the new opening value of the valve 42 is reached. A constant load is thus generated on the spring, which is constantly acted upon by the valve, and this

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constant work causes vibrations and overpressures due to the inertia of the system,

In practice, this system regulates the amount of liquid as a function of the output from the pulling unit of the catenary, which is true if one takes into account that only the excess amount is drained off during the remaining amount is used by the shovel.

Only the shovel was considered in the description

L · drawn, but it's obvious! that instead of the blade, a straight chamber cylinder, torque generator, etc. can be provided to achieve the same effect,

Even though the system described above responds with oscillations and decelerations and generates excess pressures, the invention can be exploited in such a way that the amount entering the thrust chamber is constantly regulated and at the same time the valves 42 and 42 * are biased. By a constant regulation of the in the thrust chamber As a result, the aim is to introduce only the amount of liquid into it that is necessary

w to maintain the pressure proportional to the output taken from the traction unit. If the preload of the springs acting on the valves 42 and 42 is constantly changed, the same sequence is implemented again, but the functional relationship is changed insofar as in practice the bucket conveyor is only allowed to move back in the event of an excessive material fall.

A 28 -

as

It has already been stated in connection with the description of FIG. 2 that in the normal thrust unit shown in this figure, the valves k2 and 42 "serve to keep the pressure constant and to absorb the pressure increases which then occur in the blade, vrexm the Bechear conveyor swings back due to a material slide.

Henxi the valves hz and 42 * are only subjected to this last-mentioned function, then a perfect regulation of the thrust is achieved, which always remains proportional to the requirements of the pulling unit «

The following is the practical implementation of a first preferred scheme to better explain the Described advantages achievable by the invention.

The scheme according to FIG. 7 shows a thrust unit from the 2, which, however, is used for the purpose of assigning the pulling unit to that described in FIG. 6 Way (or Fig. 5, since one is a natural improvement on the other) "

The controls going to motor 85 ("^ ig · 6) can be modulated continuously or periodically «The difference between the two systems consists essentially in the precision with which the signals, in particular in terms of speed, addressed, should be, and in the cost »

The following is an example of description assume that the modulation is continuous and that consequently the motor 85 continuously control signal ©

BATH

29 »

1954U6

receives and forwards that there is no discontinuity and that consequently the control, which reaches the engine and depends on the output of the traction unit, is continuous. It is clear that the motor transmits the impulse to the shaft on which the cams are attached ( only two cams 87 and 87 * are shown in FIG. 6 ) via a reduction, since always with a certain delay and inertia

+ ■ must be addressed in order not to excessively use the system

sensitive to design.

Excessive sensitivity would lead to a sudden response, which would affect the resistance that the cups encounter and could reduce or increase the force required for the pull. a new modulated correction impulse would be produced, which would result in a reverse reaction, etc., without interruption and without lengthy adjustment *

If, on the other hand, there is a certain inertia, any impulses or disturbances are read, but in the automatically compensated for the final control signal which the cams transmit, it is thus a softer and more trouble-free one Functionality achieved,

IDs already mentioned that the engine 85 has a Reduction the cam controls (in Fig. 6 the cams are

87 and 87 "shown).

In Fig. 7 the cams with the beacons 87 - 87 »

88 and 88 ». In this and in the following figures

m / m

m 30 -

«AD OWOlNM.

19.5AH6

For the sake of simplicity, the cams are shown as circular, in reality their shape or, better, their increment of each major part corresponds to the allocation law established for the thrust unit, which, depending on the results to be obtained, can be linear or exponential. The cams could, for example, applied to almost all 36O be ^0, and not just 180 °, wieyfes is the case in the drawing for simplicity.

The motor 85 thus overtakes the control, which to him 'got to the cams 87 and 87 * and 88 and 88 *, the are not shown coaxially in the drawing, but it could be that an indicating a reduction in the thrust pressure Impulse results in counter-clockwise rotation, whereas an increase is necessary The impulse indicating the thrust results in a clockwise rotation of the cam. A reduction in thrust is required if the drive motor of the chain system (Fig, reference number 80) indicates that the current consumption is excessive, d, h, if he indicates that he is under a greater burden than is exposed to the specified load. However, it is necessary to increase the thrust when the drive motor works below the specified value,

Xn Fig, 7 the cams are shown in their top dead center, that is, if they rotate in one or the other direction that they do not convey an increment to the organs in contact with them, which means

that the Zugaggregat above the set optimum conditions while working, has been transported away until the whole material, thus the reaction force against the forward movement ^v, to which the Kettenwerlc meet, is reduced and the motor receives no pulse 85. In practice, the position of a momen tane static position shown in the figure is caused by a sudden and excessive slipping of aggregate material w ± rd _# ™ is in the ^ the operation olge the thrust units according to FIG described. 7 As the top ^T of the Nooke (PMS) otpunkt is the position to understand which dista farthest from the rotation center of the cam, corresponding to the m _a imum Inkrenient, which may be the Nooke, while as the lower ot $ oint (PML), the rotational center to the on The next position is to be understood with the increment zero, According to PIG, 7 the cams, as already mentioned, are in the position PMO,

For a better understanding, it is explained that when the conveyor swings out, the cams are in the PMI position, whereas when the conveyor is exposed to a load that exceeds the load set for optimal conditions, the cams, as according to ^ ig, 7 _{t are} in the PMO position,.

In the following, the method of operation of the invention Improvement explained.

If the bucket conveyor (12 in ig, 1 to; 3 and k) is pivoted without it hitting the material to be loaded ^

- 32 -

QRiOiNAl.

If the bucket chain system is rotated without picking up material, the condition exists that the pulling motor (27 in Fig. 1 and 80 in Fig. 6) under the lowest load and that the motor is only required to increase the resistances of the System, which represented an easily available basic value which, even if it changes over time, never overly rejects,

If desired, this deviation can be made by means of a suitable Variators in the comparison disableser 22 or in the balanced Wheatstons * bridge 84 are introduced, which introduction is known to the person skilled in the art and can be carried out with conventional means.

As long as it is communicated by the determination unit 82 that the pivoting takes place without a force being demanded from the pulling motor of the chain mechanism that is only slightly higher than the preset minimum, the cams are in the PMI position and it is therefore passed through the flow regulator 90 the correct amount of fluid required to keep the thrust pressure (e.g. k or 6 at) at the required optimum value,

The flow regulator, for example an axial version with peripheral recesses that act on a membrane, must have a low sensitivity to the Have viscosity fluctuations of the 01s.

The size of the flow controller is obtained ^ by starting from the basic values for the calculation of the thrust, which is to Verden the BecherfÖÜerer, undzwar1

- 33 -

Void displacement speedj required thrust for Maintaining this void speed j maximum thrust, portable by angle system. Type of hydraulic Oils *

For example, assume that the angleJLver displacement speed in the empty state 3i5 ~ ^ seo, is and that the required thrust in the empty state 'in the size-P Order of 25 - 30 kgm, whereas the maximum thrust, to which the system can be subjected, at 900 - 1000 kgm lies.

Based on these values, after determining the counter pressure at which 38 must open (for example at 2 at) and knowing the surface of the blade 36 (which could also be a piston), it is easy to apply the thrust pressure in the empty state and at maximum load calculate. In order to explain the improvement according to the invention in more detail, it is assumed that the counter pressure which the opening of 38 and 38 *. causes, about 2 at, that the pressure that has to act on the blade 36 to achieve the required minimum thrust is 6 at (k at effective thrust + 2 at counter thrust) that the flow rate required at this pressure is 2.5 1 / win and that ultimately the maximum pressure to which the shovel has to be exposed has to be 27 at (25 at thrust + 2 at counter thrust).

The pump gives; constant an amount of liquid of approx. 3.0 1 / mln at a pressure of the above, 20 at (this pressure can be in Depending on the structural features of the unit and vary depending on the rules that are applied),

which pressure from the maximum pressure valve 33 (or 33 * with reversed Functionally) is kept constant, however the counter valve, which only work on return, is set to 2 at are set, what counter pressure shock vibrations, Eliminates vibrations and abnormal puncture conditions.

Egler by ^R 90, at the front of a pressure of 30 and behind which such prevails at 6, reach 2.5 i / min when it is fully open, that is, when the cams take the pitch PMI, wherein the 6 at automatically set, since the system at only h for the movement at the set by the through-flowing quantity in the chamber 35 velocity requires that pressing serves consequently, to wave the Trögheit and frictions, which counteract the Verschwenlten of the system.

When the bucket conveyor begins to remove material from the ground, the traction motor tells the cam that it is necessary is to reduce the speed of movement during the DrucIcT) Dη increases alone in the chamber 35 because by the Arrival of fluid in a larger amount to progressive Availability of space creates an upper pressure.

To reduce the speed of movement, twist the cams 88 and 88 * move in such a way that the flow regulator in the diaphragm 89 is advanced by which displacement the passage opening and consequently also the flow rate is reduced, the latter also by the diminished ^ \ 1 », twisting the two faces of the panel 89 prevails, is diminished.

- 35 -

This * ¹ reduction in performance in chamber 35 results in a lower angular movement of the bucket conveyor, which can work under stable conditions of use or above or below these «

If it is in a stable state, it means this that with the new swivel angle speed that Bucket chain system requires the entire intended performance from the pulling unit.

If, on the other hand, the conveyor is below the optimal

Value, the cam 88 (or 88 ·) rotates in the opposite direction to the clockwise direction, that is, it tries to get into the position PMI. This has a greater flow rate and consequently a greater Winkelverschubgeschwindigkeit and hence a greater increase in the proportion movement zwieshen the one and the other cups with an automatically greater power requirement and greater from the motor absorbed power for the ^F olge,

If, on the other hand, it is indicated that the engine is already absorbs a greater power than the optimal power, the cams 88 and 88 * rotate up to the position PMO and stay there until the capacity used is below the intended optimal capacity, whereby in the position PMO the cams the flow rate through the Knob 89-90 is zero or close to iJull.

Since the ratio of the duroh 89 - 90 flowing liquid it erne nt θ to the maximum value of the flow rate (which from

- 36 -

INSPECTED

Maxi space fluctuates from 2 _# 5 ~ 0 1 / min) and is equal to or approximately 1 to the unit volume of the enlargement of the chamber 25, in particular after the blade has already performed about 30 - 45 ° of rotation, the result is that thanks to constant control of the Flow rate as a function of the thrust and the rotation of the blade, the pressure in the chamber 35 from the set minimum value (in the example 6 at) to the predetermined maximum value (in the example 27 at) constant and fluctuates several times in a working cycle, and this only in Reference to the message of the pulling motor of the catenary.

Since the pressure in the chamber 35 fluctuates in relation to the reciprocal pressure of the control unit 90 and the diaphragm 89, which ratio follows an exponential law which is characteristic of the sum of all the factors cooperating in its formation, it is necessary to adjust the controller kZ bias so that he. is adapted to the requirements of the pulling unit.

The controller k2 in this preferred unit assumes a partial function in relation to the processes in the unit shown in FIG.

While it was used in the unit according to FIG. 2, to regulate the speed as well as it the Allow bucket conveyors to move in case of oversize To free avalanche-like material slippage, it only fulfills in the preferred embodiment of the unit the last mentioned puncture.

For example, suppose that the mutual Location of the various organs that work together to build up the pressure at 35 (regulator, diaphragm, chain, aggregates, Traction unit etc.) at the moment X had built up a pressure of 10 at in the aforementioned chamber and that a Moment after X + 1 an avalanche-like material slide occurs, which buries the catenary, whereby due to the

W structure of this Instabili $ ätsbedingungen the cams received orders to move into the position of PMO, which is done but the inertia Augrund with a certain delay.

However, after controller 42, in the position assumed by the cams at time X + 1, has been adjusted to 10.5 at (in the present example, it could, however, also be set to 11 or 12 at), chamber 35 found a ground the material Rutsches which the ^K spilled ettenwerk, a sudden rise in pressure take place, the more rapidly the iat ala

^ Response of the cam to the impulse of the motor, which this was supplied by the control system.

This approach has led to the counteraction of the control valve kZ being overcome , which enabled part of the liquid to exit via 43 »

This liquid seepage becomes less and less until dr canceled himself to compensate for the thrusts on 42, in the In the meantime, however, the conveyor was able to wilt almost backwards (thanks to the special "nasal formation of the cups, which

00024 /
-3 * -

also produce a radial thrust component that was to which formation already made according to the patents No 673366 and 821750 of the applicant), as in the chamber 35, the reaction does not exist, but if there is no discharge over 32 -. 42 - would have occurred 43 , would be present.

"When the Nookes gets into the PMO position, if the sponsor has not been there in the meantime has released, the control valve 42 is tared in such a way that it withstands the intended maximum pressure, which pressure in the chamber can be present when the material avalanche It is excessively large and the sponsor is because of the drought Do not free the volume of material to be removed in time could. In this case, the sponsor transfers by the Reaction of the settling of the pile of aggregates created by the cups continues, the shaft 45 and consequently the blade 36 a constant reaction, which can lead to the creation of a "counter pressure to the valve 42, the greater than the initiated jerk and at which the liquid flows out via the line * 43, creating the correct location of the conveyor in relation to the pile of aggregates is restored, and consequently the thrust caused by the cups equal to (or less) that by the Regulation of the cam in PMO predetermined or the preset Maximum pressure is.

Should a finer regulation and a better reaction

- 39 00882W

to

can be achieved on the requirements of the conveyor, namely a regulation which enables a real control of the thrust system and consequently a quick restoration of the optimal conditions, which conditions can be delayed by the sole control of the valve 42 by the cams or do not meet the actual requirements de: e System, the valve k2 can be servo- operated so that it is self-regulating by the pressure prevailing in the pressure chamber.

This self-regulation reaches the VentiX via the line 93 "which regulates the response of the valve and delays it due to its small dimensions. In practice it works this line 93 "as a flow regulator, which the principle of the resistance opposite to the flow.

The controller 93 "is used on the rear of the

Valve k2 builds up the same pressure as in line J2 "'(see Pig, 8), the provided spring consequently has a different function than that of control valve k2 according to PIG, 7, while in the solution shown in Fig. 7 the regulator is from the outside is regulated (by the noise voltage of the ^ leather) such that it opens only with a slightly grbsseren pressure than the chamber in the push ruling according to have the solution according to Fig, S the spring is a fixed V _ORS p _Annun g and is at any pressure on both sides of the regulator k2 of a fixed value which corresponds to the maximum tolerated in the thrust chamber / ^ ψ .

■ 0008 * 4 ^ 1 * 77

- ko -

The solution * shown in Fig. 7 is not common to all Aggregates can be used, for example, when there is a pressure of 15 atm in the thrust chamber and the conveyor is in a thrust demand position and a material, avalanche slips off, the train motor reports that it is necessary is to reduce the flow rate in the thrust chamber at the same time the cups have created a reaction to their release, which results in an overpressure in 35 expresses what overpressure, for example equal to 5 at (so that 15 + 5 = 20 atm prevail in the chamber) the valve opens so that the liquid exits via line 43.

^T he liquid flows further out and sets the propulsion thrust down, in the meantime, however, the cams set in motion until they due position PMO that is, the road position, reach them whereby the inflow through the line 43 blickleren, since in the position PMO the cams set the control valve 42 to an opening pressure of more than 27 at corresponding to the maximum thrust.

With the variant shown in ig, 8 can be achieved

r
be that at certain, caused by the mug

Counter thrust values (logically high values) the time required for the transfer of the pressure increase to the rear of the controller kZ, such that, even if liquid flows out above 43, the pressure is always above the ^ F that is required for opening the Vantiles 42 required

BATH ORIGINAL

This has the consequence that in the chamber 35 also a lower pressure than that at the moment when the avalanche collapses can build up pressure, which affects the conveyor the opportunity is given to move back quickly enough, to restore the optimal conditions,

Another improvement is obtained by using the two systems related to the cam and the self-regulation combined, thus the advantages of both the one and the of the other system, however, this solution is rather complicated and involves a difficult one Regulation with itself.

The problem now arises, the conveyor quickly from Drop piles of aggregates when the command arrives indicating that this $ 4rt of aggregates is not more should be loaded »

Since the cams, as stated above, have a certain inertia, would at a Umker the .Strömungsrichtung the pump 3 "! Ι d" h _t when her oil under pressure not as before through the line 32, but by the line 32 ^{would feed r} , the case that the flow regulators 90 could be in any relative position between PMI and PMO and that before they return to PMI, a certain amount of time elapses during which the conveyor continues to charge.

To prevent this, arerei lines 93 and 93 · provided which runs "direct the liquid into two chambers in soft jewe11β a piston $ 2 and 92 * In the shown -

Embodiment two chambers are shown "of the system however, it can also have a chamber with four openings and one Work the same with two lines that fulfill the same function of the two chambers.

In the example shown in FIG. 7, two pistons π (! «\, Which cause the closure of the branch line $ k and the opening of the branch line 9k * are provided . In this case, the liquid in the line 9 ^ * Move in the | direction against the blade chamber, but not in the opposite direction, because the line 9I 'blocks the flow.

If now by means of the ^ umpe '31 · the direction of flow the liquid has been reversed, this flows over 9I * through line 9 ^ 'and enters chamber 37, whereas the liquid of the chamber 35 exits from 38 ', the Drain remains relieved.

This continues until the piston 92'f - since the pressure opposite to it ^{is relieved via line 93%} and line "93, shifts and blocks line 9h . In the meantime, however, cams 88 and 88 »has returned to the PMI position and the liquid again passes through the flow regulator 90 * - 85". In this way, it is quickly separated from the pile of aggregates, after which the normal radial empty displacement speed of the bucket conveyor is recorded.

For the sake of clarity, the lines 93 are shown

and 93 ^f interrupted at AB, the A'B * GLiS continuation of the same.

12-77

1954H6

in Fig. 9 ^ - ^s * illustrates a further solution which makes use of the improvement and which makes use of the regulation of the flow rate, while in Pig, 7 a solution with a pump 31 ¹ ^ with a fixed flow rate is shown, relates to Pig «8 a solution with a pump 95 with variable flow rate«

Using the values cited earlier, it is assumed that the pump 85 in the PMI position of the cam 88 is 2.51 / min at 6 at and 0 T / min. at 27. ^a * pumps "

In reality it delivers a minimum amount at 27 at in order to maintain the pressure and to overcome the resistance, however, this delivery rate does not result in any noticeable radial displacement (if you start the charging cycle a bucket conveyor), it is therefore negligible and is assumed to be 0 1 / min «

Zuin easier understanding of the invention is shown in Fig. 9 illustrates a vane pump defined by the movable part Λ 03 and, however, the rotor 95 pump formed could also be a type with axial pistons, with the radial piston or with linear piston, depending on the materials used for carrying out the invention Establishments that can make one or the other Iloung more economical "

It is only of interest that the pump is variable Flow rate emits and that this © variability through the power consumption of the traction motor by means of de «accordingly shaped cam 88 is conditioned "

- ülf- 008824/1477

_BATH ORIGINAL

In Fig. 9, the pump is approximately in the neutral line split and it just turns around to maintain the pressure reached in line 32 "

The pump has the same function as the flow regulator of the example according to FIG. 7, with the only difference that, while the circuit up to the flow regulator 90 must always work at maximum pressure and maximum flow, that is, the motor that actuates the pump 3I is always loaded, the pump actuating motor is loaded proportional to the power required by the system flow in the solution according to Fig _# 9.

Fig. 9 shows that it is the stationary part that is moves under the action of the cam 88, in practice each of the cams could also act on the rotor, whereby the board is left in its position, but these solutions are well-known measures, their further explanation calibration unnecessary.

The counterpressure against the cam 88 is created by the spring 6 and the travel limiter, that is, the control of the zero point is given by an adjustment system 97, for example a screw and nut. This setting required to compensate for play and wear and tear requires that the squat 88 acts on an elastic element, which in the drawing, for example, is a leaf spring 104. The valves 42 have the same function as the analog valves in the example described above and can therefore use the Constructive training described there

“AD

The control of the cams. 87 - 87 * and 88 takes place like in the example described above, only needs to be in the case of order ~ Reversing the pivoting direction, the cam actuating motor can run at two speeds to the cam quickly to the PMX position and consequently to bring the pump to maximum flow rate.

This can be done by the arrangement shown in FIG

^ are avoided, geraäss which the elastic function is taken over by the piston 98, which is connected to the pressure side of the floating piston 99 displaceable in the chamber 100. The chamber 100 is connected to the pressure side and the suction side of the pump. The piston 98 is acted upon by a counter-spring ' ¹ , to overcome the bias of which in the chamber 100 a pressure is required which is above the set counter-pressure that arises in the second blade chamber Allocation Act and the area in which this Act is applied *

ψ If this law for the entire work area validity have soil ₁ as the thrust pressure is equal to about 7 to $ at _t whereas the pressure corresponding to the maximum deflection 27-28 corresponds at, the difference value between Voapannungsbiegung and maximum Working Curve gewähl as a function of the increase ; which is given to the cam between the two extreme points PMX and PMO ¹ * When the pressure side of the pump in the chamber is reversed

1954H6

builds up, a minimum pressure (in this example 6 at) on ι which moves the piston 99 and thus a blockage on line 101, but this bridge is not large enough to absorb the force of the return spring of the piston 98 to overcome, creating this opening, which is due to the higher pressure prevailing under the piston during the charging phase, it is zeroed and the pump immediately begins to deliver liquid into the chamber 37, thereby eliminating the inertia of the cam 38 will" *

Mentioned piston also serves eventualle pressures, which in the circuit due to material avalanches that echerfftrderers carried out the return movement of the ^B aufbauen- is to catch 'kSnnten serves "

Using the solution according to Pig, IO becomes practical in the reversal phase of the swivel thrust a specification on the Movement of the chamber achieved, causing the for return Dead times required in the PMI position can be reduced.

Using the solution shown in Pig "10, a further advantage is still achieved * In the case of übermäsaig large material avalanche in the thrust chamber, a _v constructed overpressure which transmits rapidly to the pump, the transfer, however, takes place on the piston 98, the Pre-tensioning of the spring overcomes and shifts. In reality, eat is because the piston 98 against the cam

9824/1277

BATH ORIGINAL

is pressed, not he himself who is shifting, but the jacket unit 103 * »where this relative shift brings about a reduction in the delivery rate of the pump, which reduction can also reach a zero value » The reverse mode of operation occurs if the conveyor's aggregate suddenly gives way does not work at full load, which means that the drawer 25 of the example the pressure drops and as a direct consequence also ™ in the chamber 100j in which case the springs gto "die move mutual position between rotor 95 and chamber 103, where they lead the cam and an increase of the flow.

It is clear from the above that a precise locking between the pulling unit of the catenary and the pushing unit can be achieved, which locking can furthermore be perfected using the automatic mutual assignment of certain parts of the pushing unit,
^ There are now two further improvements to circular

Drinks, which are shown schematically in patent application no. 68521 A / 68 Sar, and relate to the functioning of the traction unit ° * of the chain system by means of a hydraulic motor, described, "\ ■

In this case both the rotation of the chain mechanism and the pushing movement are maintained hydraulically «

This solution automatically entails two more exercises , those in Figs. N and 12 in the for understanding

• 0098 * 4/1277

- kB -:

ORIGINAL

of the invention shown in the best and simplest form are"

This Lftsung automatically brings two other solutions is represented strength in the most appropriate for clarity of explanation in the form of ^F, 1ΐ and 12, "

According to these two statements, Fig. 11 shows a single one Control center with locking of the thrust circle and Fig. 12 a double control center with one thrust circle, which is assigned to the equipment group.

The functionality * of that circle is described first, which has only one control center and is shown schematically in Fig. 11.

The circle has two main components, namely one Control circuit for the rotation of the chain system and a control circuit for the control of the swiveling thrust,

The only motor 111 actuates the only pump 110 which takes the oil from the container 121. The liquid is pumped under pressure into the liquid divider 124, which divides it into the lines 117 and 118 according to a previously determined, constant fixed value, whereby in the line 118, on the basis of the values given previously, for example, delivers a flow rate equal to 2.9-3 \ t / min at approx. 30 at, whereas in the line 11? the amount is introduced which depends on the speed at which the engine must run and on the characteristics of the engine itself.

The liquid divider 124 divides the constant

000824/1277

so

amount of the pump 1 to in two constant flow rates, those in lines 117 and 118 independently of the in the lines are fed before and after prevailing pressures, ".

Via line 1Ϊ7 the liquid passes to the hydraulic motor 1i4 'after it passes through the electro-hydraulic valve 11.3, has, which could also be omitted, but which is provided forward release the Sohubaggregat in Betrien and; Exclude pulling unit.

The fluid passes over from the hydraulic motor 114 the line 120 to the control valve for the minimum operating pressure of the hydraulic motor 115 and then to the. Filter 116 and finally again to container 121 »

THE control valve 115 is required to be in the line 118 to create the maximum idle operating pressure, if that Chain mechanism is pulled for a short time, in which case before and after the flow regulator 89 »90 the necessary

P would build up, which is why the valve 115 is tared to 29-30 at fe, whereas the exact regulation of the excess of flow rate and pressure in the line 118 takes place by means of the control valve 132, which the supply line and the discharge line 119 and the container via there ^F ilter 116 »short-circuits,. '*

The amount of liquid introduced in 118 is consequently constant both in terms of volume and in terms of pressure. Xn of the drawing is sohematisoh indicated that the chamber under pressure is the chamber 35;

000824/1277

" % original

1954H6

The liquid reaches the chamber 35 via the flow control unit 90 and the diaphragm 89 due to the conditioning which is imposed on it by the pressure existing in the chamber 105. The chamber 105 is fed iron of the line 112 and is therefore acted upon by the pressure! Which prevails in front of the hydraulic motor, which, since it is self-regulating with regard to LED absorption and constant speed of rotation, constant as reported in the power required for the A P before and after the motor.

The increase and decrease in pressure in I05 therefore brings about a yield or an expansion of the spring which acts on the flow regulator 90. These Changes in the spring tension cause a larger or smaller opening of the flow cross-section through the Hegel diaphragm unit 89-90,

The greater or lesser sensitivity of the servo control system can be achieved in two ways, either by taking the power 112 up to consumer parts, for example the chamber 105, dimensioned in such a way that those losses of power arise which are suitable for the peaks to steam and to verssfigern the response reactions or by a suitable diaphragm is used, which regulates and compensates for the incoming impulses and modulates and delays them. In the example shown, you can only see one line that is dimensioned in such a way that the damping by means of continuous Latency loss is received and it is

• 51 - 00 9024 / 127.7

.- ** BAD ORiGlHAU

1954HS SJ

Ofjpensichtlicli that if the Woung takes place in the manner shown in Fig. 11, the connecting line between 105 and 105 * must be designed in such a way that no further moments of inertia arise, so that the two thrust chambers are not subjected to two different locking laws.

To reverse the thrust circle, i.e. to quickly set the conveyor down from the pile of aggregates from which it has previously been loaded, a bleed valve or an electrohydraulic valve or other door is suitable for this purpose Commercially available organ used. The shape shown in the drawing figure 11 is therefore only for example and. represents a valve to which two coils 108 and 109 are assigned. Since the coil 108 is actuated in the case shown, the slide has connected the lines converging at Gr * and F via ^{line CC 1} and the lines converging at G and F * ^{via DD 1.} If one ie the _U Sp energized ontregt 109 and the coil 108, the slider is pulled in the position for the reversing of the cycle, the terminal CC "that connects the ends G and G * whereas the terminal DD * the ends F and F * connects with each other "In this way the connection of the circle 118 with the line 32 * and the outlet 11 $ with the line 32 was obtained." When the thrust crisis is reversed, the lines 92 and 92 * come into action in the aforementioned manner, whereby they allow the liquid to enter the chamber 37 quickly

8 2 4/1277

- 52 -

So be quick, the bucket and therefore the loader conveyor to move »

The valves 42 and 42 * function in the same way

Way like those shown in ig, 8, you can but

■ f - ·

more can be assigned to the pulling unit of the chain system

With such a perfected system, the pump always delivers that fixed flow rate at the various pressures as a function of the requirements with regard to the Leifroongs output of the hydraulic traction motor IkO of the chain mechanism, whereas the electric motor that actuates it is proportional to the pressure that is in front of the hydraulic one Motor 114 builds, is acted upon.

The minimum pressure at which the pump works $ is the Pressure of the maximum taring of the thrust circle with a Pressure close to this minimum pressure,

If you want, you can use the pump at a lower rate Apply pressure and then adapt them to the requirements of the Adjusting the cycle, such complicated perfectings however, do not provide any benefit other than part of a commissioned driving force for the system which force, however, in the example shown in the pressure relief valve 115 is posted.

With regard to this cycle, this applies in context with what was said in ig «7, i.e.

4! »

that it is conditioned by a static flow controller, which controller, in order to work properly, requires a certain Δ ρ before and after the Btonde,

000824/1277

Moreover, this system provides a complicated circuit, long Z _u i _e £ tongues and long Ruoklaufleitungen, alkalis "which along the machine with it.

Am circuit on the principle of the pump with variable Flow rate, as described in ig »9, is shown in FIG.

The circuit has a main part, which is capable of the hydraulic motor 1 of the tk Kettenswerkes in function% to set, and a sub-part i which the blade 36 is actuated. The two circles are connected to one another and the lifting circle is assigned to the main circuit via line 129, which acts directly on the delivery rate of the pump.

As with the pump shown schematically in ^ ig * 9 a vane pump is also shown here, this pump could however, it can also be a piston pump or another pump suitable for this purpose.

The minimum flow rate is regulated by means of the adjustable travel limiter I38, while the maximum flow rate is regulated by acting on the limiters 136 the traction motor 11 ^ uea chain mechanism prevailing pressure is locked via the line 129, which connects it to the chamber. When the pressure in the chamber 135 is increased or decreased, the return spring 14O is more or less loaded with a change in its tension.

009824/1277

When changing the tension or the height of the return spring \ kO it is achieved that the mutual position between the body of the chamber 131 and the piston 14O varies. In order to change this mutual position to a noticeable extent, however, it is necessary that the pressure in 135 also overcomes the force opposing the spring 137. The pressure that builds up in front of the traction motor 114 of the chain mechanism to cause a disturbance in the feed system of the thrust chambers must therefore overcome the force of two peder organs 137 and IkO .

If it is desired to lock only the pressure side of the pump with the requirements of the traction unit, it is not necessary to provide the size of the counter spring 140 and the piston tjk can therefore form a single body with the housing, which receives the sliding part 131.

If, on the other hand, there is a need for reversal and a better and more complete control system, the system previously described and shown in Fig. 10 is used, whereby it is necessary to double the size of the counter springs, as they are iü ± t 137 vma. IkQ is indicated to be provided. If the pressure in the line 125 rises or falls , there is an automatic rise in the chamber 132 and consequently in the chamber 141. In this case, the piston 13 floats and only comes to the stop on the housing in the case of the minimum pressure of the Sohubkreiellauf, which the sliding part 13I receives ' _t when the pressure is increased

- 5 * - 00 9 824/127

in the line 125 ″ a pressure builds up in the chamber 1 k 1 which, by adding to the pressure prevailing in the chamber 135, acts against the spring 137 Increase or decrease in the regulating effect which causes the pressure in the chamber 135. The same effect is therefore achieved _f as that provided in FIG.

w suggested system, which also applies to the reversal and the dimensioning of the pressures and the vege. Since the servo control according to Pig, 10 is mechanical and that according to Pig, Ϊ2 is hydraulic, in practice, apart from a few minor variants, the same considerations apply to one system as to the other.

The foregoing were therefore four extremely simple and prd & ic perfecting of pulling units and pushing units explained by bucket conveyors.

As can be seen from the description of the accompanying figures

. proceeds, they are designed in such a way that the parameters of the Use of the pulling unit and consequently the general parameters of the hourly output of the swivel conveyor ^ Lm general and the bucket conveyor in particular is used to the maximum will.

00982A / 1277

original

Claims (1)

Patent claims * I 1,! Loading device for bulk goods present in orm ^ - S r Aggregates, consisting of a stationary holder »a swivel arm, which has a conveyor for receiving the aggregate material and for the radial or, if necessary, vertical transport of the same in the vertical plane of the arm to a predetermined point, organs for connecting the arm to the holder» such., characterized in that the arm is rotatable about a fixed vertical, sub-vertical or slightly inclined axis, which is carried by the mentioned arm and organs for operating the conveyor by giving it the necessary movements for the removal and transport of the aggregate material are that the movement unit and the ^T ransportaggregat functionally locked together such that the strive to maintain in any case, in general, optimum working conditions and restore, 2 »Loading device according to claim 1, characterized in that that the locking of the two units is realized by using one of the variables as the variable control variable, 009824/1277 - ~ 57 · * ■ '■ ■ which the functioning of one or the other Express aggregates, is used and that for Maintaining or restoring optimal working conditions at least above one of the changeable ones, which expresses the functioning of the other unit, is acted upon, this effect being above the variable of the other aggregate is so affects the predetermined value of the control variable is maintained or restored, the latter moreover through a self-regulation of the assigned aggregate is completed. 3 »A loading device according to claim 1 or 2, characterized overall • indicates that the locking of the two units is realized by members for the decrease in the control variable of an aggregate, a" uswertungsvorrichtung which the receive entrance ^s determined by these organs ignal , and organs for the transmission of the output signal to the other unit are provided by the Auslertungseinrichtung, such that the desired modulation of at least one of the variables of the other unit is generated, kt loading device according to one of claims 1 to 3, characterized in that the maintenance device consists of electrical and electronic organs and of a - 58 - 009824/1277 Combination of the same inks indander and / or with mechanical Organs consists " 5i loading device according to one of claims 1 to 4, characterized in that the A _USW processing device consists of hydraulic organs or a combination thereof with the organs according to the preceding claims, 6 · 'loading device according to one of claims 1 to 5 1, characterized in that the control variable is read as an electrical variable, preferably as the intensity of the current, and that organs are provided for cleaning the reading of this variable from disturbing palctors, 7, loading device according to one of the points 1 to 5 »* characterized in that the Steüerungsvariavle as hydraulic variable, preferably as pressure, is read and that organs for cleaning the reading of this variable are provided by disruptive factors, 8, loading device according to one of the initials 1 to 7 » characterized in that the control variable from Pulling unit of the catenary system is removed and used, around the unit, which is used, the pivoting thrust to cause locking with it, taking as a control variable essentially that of the traction unit for operation 009824/1277 - 59 - . BÄÖ ORIGiNAL 1954H6 Co the driving force required by the conveyor's receiving elements is used; 9 · A loading device according to any one of claims 1 to 8 _t characterized in that the Schubaggre & at "is associated by means of cams, which act in the sense that it constantly control the amount of entering into the thrust chamber liquid and arriving in a ratio to the Zugaggregat Bring inlet, which effect is expressed either by a flow regulator or a variable flow pump, 10 * loading device according to one of claims 1 to 9, characterized in that the thrust unit has a Branch is assigned, which the assumed control variable, in particular the operating pressure of the hydraulic motor, to the control units of the flow, these are actual regulating organs or pumps with variable flow rates, transmits, 11. Loading device according to one of claims 1 to 10, characterized in that the fluctuations of one of the variables of the thrust unit, in the special case .des pressure that builds up in the thrust chamber _{t are used} by the unit itself to access the intake from the pulling unit to complete or to improve the performance of its aggregate and moreover 0Q9824 / 1277 - 60 - ■ · ■ *. SM> to effect a rapid reversal of the pivot direction and around the overpressure control valve and return valve of the aggregate conveyor in the event of excessive material avalanche to bring a relationship. 12, loading device according to one of claims 1 to ti, characterized in that the thrust unit is the pulling unit of the chain mechanism also for the supply of the drive fluid is assigned, in which case both are fed from a single control center, which via a flow distributor or via two combined pumps constantly supplies the same proportional amount of liquid to the two consumer circuits and whereby the amount of liquid per circuit is predetermined independently of the pressure differences * öind,. "■■ * ■■ 1 * 1, loading device according to one of claims 1 to 12, characterized in that both the pulling unit and the thrust unit has its own anti-vibration source in the form of owns two independent pumps. - 61 ~ '009824/1271