Classifications

• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
  • B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
  • B06B1/00—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
  • B06B1/18—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency wherein the vibrator is actuated by pressure fluid
  • B06B1/183—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency wherein the vibrator is actuated by pressure fluid operating with reciprocating masses
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B03—SEPARATION OF SOLID MATERIALS USING LIQUIDS OR USING PNEUMATIC TABLES OR JIGS; MAGNETIC OR ELECTROSTATIC SEPARATION OF SOLID MATERIALS FROM SOLID MATERIALS OR FLUIDS; SEPARATION BY HIGH-VOLTAGE ELECTRIC FIELDS
  • B03B—SEPARATING SOLID MATERIALS USING LIQUIDS OR USING PNEUMATIC TABLES OR JIGS
  • B03B13/00—Control arrangements specially adapted for wet-separating apparatus or for dressing plant, using physical effects
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B03—SEPARATION OF SOLID MATERIALS USING LIQUIDS OR USING PNEUMATIC TABLES OR JIGS; MAGNETIC OR ELECTROSTATIC SEPARATION OF SOLID MATERIALS FROM SOLID MATERIALS OR FLUIDS; SEPARATION BY HIGH-VOLTAGE ELECTRIC FIELDS
  • B03B—SEPARATING SOLID MATERIALS USING LIQUIDS OR USING PNEUMATIC TABLES OR JIGS
  • B03B5/00—Washing granular, powdered or lumpy materials; Wet separating
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B03—SEPARATION OF SOLID MATERIALS USING LIQUIDS OR USING PNEUMATIC TABLES OR JIGS; MAGNETIC OR ELECTROSTATIC SEPARATION OF SOLID MATERIALS FROM SOLID MATERIALS OR FLUIDS; SEPARATION BY HIGH-VOLTAGE ELECTRIC FIELDS
  • B03B—SEPARATING SOLID MATERIALS USING LIQUIDS OR USING PNEUMATIC TABLES OR JIGS
  • B03B5/00—Washing granular, powdered or lumpy materials; Wet separating
  • B03B5/60—Washing granular, powdered or lumpy materials; Wet separating by non-mechanical classifiers, e.g. slime tanks 

Definitions

• the invention relates to a device for cleaning, discharging and dewatering sponge material from contaminated solid-water mixtures with the generic features mentioned in the preamble of claim 1.
• a cleaning machine of this type is known (DE 36 11 235C1) which essentially consists of a washing box suspended in a machine frame via vertically arranged springs, the washing liquid and the items to be cleaned being located in the washing box.
• the washing box can carry out oscillating movements in the conveying direction and in the direction of the overflow of the washing box in the machine frame, wherein these oscillating movements can also overlap.
• These oscillating movements are generated by pressure-actuated drive cylinders, which are arranged between the machine frame and the wash box.
• the oscillating movement in the conveying direction is generated by means of a conveying pulsator, the housing of which is articulated on the machine frame and the piston rod pointing essentially in the conveying direction on the bottom of the washing box.
• the oscillating movement in the direction of the overflow is achieved by means of a washing pulsator, the housing of which is likewise articulated on the machine frame and its piston rod, which is directed essentially in the direction of the overflow, on the bottom of the washing box.
• a washing pulsator the housing of which is likewise articulated on the machine frame and its piston rod, which is directed essentially in the direction of the overflow, on the bottom of the washing box.
• a complex control system is required, with which the hydraulic medium conveyed by the pump is supplied to the individual drive cylinders in a targeted manner and in a metered manner in the required amount. It is also difficult to set the oscillation of the washing box precisely for the conveying movement of the goods to be cleaned and the discharge movement of the contaminated wash water, since due to the friction-related pressure losses and the elasticity of the feed and discharge lines, the drive cylinders cannot be precisely controlled with the Hydraulic medium is possible, and thereby no exact phase shift of the respective oscillating movements of the drive cylinders can be set.
• the invention is therefore based on the object of providing a cleaning machine in which, even during operation, the oscillating movement can be set or changed exactly and in which the throughput of hydraulic medium is reduced.
• the drive cylinders of the cleaning machine essentially consist of 3 components, namely a control magnet arrangement, a control valve and a cylinder housing with a drive piston, via the control magnet arrangement, which is controlled by an electrical current, by means of an armature which is arranged movably in the longitudinal direction in a stator, a valve body is axially displaced in a valve housing of the control valve, and is thereby controlled by the flow of the hydraulic medium in the drive cylinder.
• a change in position of the armature causes a change in position of the valve body and thus control of the hydraulic flow.
• the valve body in the valve housing controls the flow of the pressurized hydraulic medium in such a way that the hydraulic medium acts on a drive surface of the drive piston surrounding the control valve, facing away from the control magnet arrangement, and thereby the drive piston is displaced in the direction of the control magnet arrangement, and thus in the direction of the first working position of the armature and the valve body.
• the valve housing surrounding the valve body is also displaced, and thereby the movement of the valve body is tracked.
• REPLACEMENT LEAF Connection connecting drive surface is interrupted.
• a displacement of the armature in the other direction, ie, in a second working position causes also a tracking of the drive piston in this direction, which is also achieved in that by the Verschie ⁇ environment of the valve body in the valve housing a second, he d S expensive magnet assembly facing drive surface is connected to the pressure-carrying hydraulic medium, whereby the drive piston is moved away from the control magnet arrangement, so that the drive piston now works as a differential piston.
• the valve housing is moved with the drive piston in the direction of the second working position and thus pushed back onto the valve body, as a result of which the second drive surface is decoupled from the pump requiring hydraulic medium.
• This drive cylinder has the advantage that it can be controlled exactly via the electrical control signals and thus phase-shifted vibrations in the pulsators can be set exactly.
• this drive cylinder only has supply and discharge lines for pressurized hydraulic medium, which, however, is not itself controlled outside the drive cylinder, but only inside the drive cylinder, so that the friction losses within the supply and discharge lines and their elasticity are none Influence the control.
• Another advantage is that the drive cylinder has only a low throughput of hydraulic medium, and therefore smaller-sized pumps are required.
• the control system can also be made simpler, since the drive cylinders are now controlled by means of an electrical current and not by means of a controlled hydraulic medium flow.
• the control device can accordingly e.g. consist of integrated circuits or the like
• the feature of claim 2 ensures that the movements of the drive piston are transmitted directly to the control valve by the integral design of the drive piston with the control valve. It is provided that the P and T connections of the control valve are always connected to the high-pressure outlet of the pressure supply unit and the tank T in every position of the drive piston.
• the feature of claim 4 has the effect that the forces urging the piston into the first or second working position are of equal magnitude. This results from the fact that the smaller drive surface is permanently connected to the high-pressure outlet of the high-pressure unit, and the other drive surface for moving the drive piston in the other direction of movement is also connected to the high-pressure outlet of the pressure supply unit. A return from this working position either to the rest position or to the other working position is achieved in that the large drive surface is relieved of pressure, so that the drive piston is moved into the other working position via the smaller drive surface.
• claims 5 to 10 ensures that the movements of the drive piston are not transmitted directly, but damped, to the screen frame.
• the drive piston of the drive cylinder engages the screen frame and the housing of the drive cylinder engages the base frame or vice versa.
• the drive cylinders can thus be installed individually in the cleaning machine.
• the damping is achieved by means of a throttle bore, which can be provided either in the damper housing or, as in a preferred exemplary embodiment, in the damper piston, which is arranged in the damper housing and separates the two damper spaces from one another.
• the damping member advantageously has a "soft", i.e. moderate and at high relative speeds a "hard”, ie. significantly increased, damping on.
• the washbox when the washbox is at rest, it assumes a rest position without a force of the drive cylinders on the washbox, for example, already in this position. attacks because the wash box is filled with the items to be cleaned and therefore the springs supporting the wash box spring in. Due to the different quantities of goods to be cleaned and in the wash box, the wash box can assume different heights in the machine frame, the height difference being compensated for each time by the damping member.
• the damper piston is guided within the damper housing in that it has a coaxial pin on one side of the piston surface and a drive extension on the other side of the piston surface, each of which is provided in one in the end walls of the damper housing Bearings are led.
• REPLACEMENT LEAF In the present case, only the time is required, which is to overcome the Disind ukttechnik 'L of the coil at the rise of current from the bias current to which the like-polarity operating current required.
• the response time of the control magnet arrangement is less by a factor of 10 compared to the response time of conventional control magnets in the cleaning machine according to the invention, since no time is required for reorienting the magnetization of the stator, the armature and the pole shoes.
• the response times of the control magnet arrangement are therefore 1-2 ms.
• claims 19 to 21 propose certain control variants which cause a periodic oscillation of the drive cylinder.
• alternating currents or direct currents pulsating through (full-path) rectification are advantageously used for the control currents.
• the armature is designed as a permanent magnet. This armature already has oriented magnetization, so that only the magnetization of the stator and the pole shoes have to be oriented in the direction of the field lines.
• claims 27 to 29 provides advantageous configurations of the coupling of the connecting element connecting the valve body to the armature.
• the coupling can be designed in accordance with the movement sequences of the valve body required for a special application.
• the valve body can accordingly at the same time with the same speed, or lagging a certain distance and with the same speed, or at the same time but with a delayed speed . -follow the movement of the anchor.
• the feature of claim 30 results in an advantageous embodiment of the pole caps closing the stator, whereby at the same time the length of the armature, which in its rest position lies between the projections of the pole caps, is determined.
• Figure 1 is a side view of the cleaning machine in a typical design.
• FIG. 2 shows an end view of the cleaning machine seen from the left side of FIG. 1;
• FIG. 3 shows a drive cylinder of the cleaning machine according to FIGS. 1 and 2, with a control valve which can be actuated by means of a control magnet arrangement, on average along the common longitudinal center plane;
• 4 shows a vibrator of the cleaning machine according to FIGS. 1 and 2, with a control valve which can be actuated by means of a control magnet arrangement, on average along the common longitudinal center plane;
• FIGS. 3 and 4 shows an enlarged representation of the control magnet arrangement of the drive cylinder or of the vibrator according to FIGS. 3 and 4;
• FIG. 1 shows a cleaning machine, designated overall by 1.
• trestles 3 are fastened, which define pivot axes 4 with lateral stub lugs.
• a machine frame 5 of the cleaning machine 1 rests on the pivot axes 4 via forks 6 which are open at the bottom.
• a lifting member 10 is pivotally articulated, which is designed as a hydraulic drive in the form of a piston-cylinder drive.
• This lifting element 10 is connected at its one end 9 to the bracket 7, and the free end 11 of the piston rod 12 is articulated to a vertical frame 13 of the machine frame 5.
• an emptying position 14 is shown, in which the cleaning machine 1 pivots about the right pivot axis 4 while lifting the machine frame 5 by means of the lifting element 10 becomes.
• the lifting element 10 can also be arranged such that pivoting up about the left pivot axis 4 or optionally about one or the other of the two pivot axes 4 is possible.
• One of the swivel axes is connected to the machine frame 5 in such a way that the fork 6 cannot detach from the swivel axis 4.
• the wash box 15 is supported elastically supported by springs 16.
• the wash box 15 is e.g. made of sheet steel and has vertical side walls (17, FIG. 2) and a wash box floor 18, which consists of two part floors 19 and 20, which form a washing trough.
• the two sub-floors 19 and 20 are placed against one another in such a way that they form a washing trough 21 in which the items to be cleaned and the cleaning liquid are located. Find.
• the two partial floors 19 and 20 form a vertex 22 at their contact line, which is the lowest point of the washing trough 21.
• the partial floors 19 and 20 each enclose an angle of approximately 30 ° to the horizontal, so that the opening angle of the washing trough is accordingly approximately 120 °.
• the partial floors 19 and 20 are advantageously provided with special floors which are adapted to the respective cleaning purpose and thus support the function of separating contaminants from the solids to be cleaned and in particular the discharge of the solids via the second floor part 20 from the cleaning machine 1.
• the wash box 15 has an overflow 23 on one side which defines a liquid level 24 within the wash box 15, the side walls 17 are raised above this liquid level 24.
• the spray direction is, as indicated schematically in FIG. 1, directed in the direction of the overflow 23, which supports the washing out of the contaminants released from the items to be cleaned from the wash box 15.
• the height of the overflow 23 is advantageously adjustable, so that the absorption capacity of the washing box 15 can be regulated.
• the washing box 15 forms a discharge opening 26. This discharge opening 26 has
• REPLACEMENT LEAF Flanges 27, which can be connected to flanges 28 of a vibrating box 29 and form an elastically sealing holder 30.
• the width and height of the vibrating box 29 are adapted to the discharge opening 26 of the washing box 15.
• the vibration box 29 is closed on its upper side by a cover plate 31 which carries a vibration device 32 in the form of a pressure cylinder-actuated drive cylinder.
• the bottom 33 of the vibrating box 29 is arranged such that it is flush with the second partial bottom 20 of the washing box 15, the washing liquid level also approximately up to the impact between the bottom 33 of the vibrating box 29 and the second Partial floor 20 reaches.
• the vibrating box 29 has the effect that the solids transported from the washing box 15 via the second partial floor 20 in the direction of the discharge opening 26 are additionally dewatered as they pass through the vibrating box 29 via the bottom 33 thereof, the water extracted from them runs back into the wash box 15. The cleaned and dewatered solids are finally fed via the discharge opening 34 of the vibration box .29 to a collection point, not shown.
• a washing pulsator 35 is installed between the machine frame 5 and the second sub-floor 20 of the washing-box floor 15, which is also a pressure cylinder-actuated drive cylinder.
• the housing 36 of the washing pulsator 35 is pivotally attached to the machine frame 5 by means of a bearing block 37,
• a conveying pulsator 40 is provided for generating the conveying movement and is arranged between the machine frame 5 and the first partial bottom 19 of the washing box bottom 18.
• the delivery pulsator 40 is also designed as a pressure cylinder-actuated drive cylinder, the direction of action of the delivery pulsator 40 also being directed perpendicularly to the first partial floor 19 here.
• the lower end of the housing 41 of the delivery pulsator 40 is articulated via a bearing block 42 to the machine frame 5 and the free end 43 of the piston rod 44 below the first partial floor 19 to the wash box 15.
• the movements of the delivery pulsator 40 bring about a delivery movement of the goods located in the wash box 15 in the direction of the discharge openings 26 and 34.
• the cleaned material located in the vibrating box 29 is dewatered via the vibrating vibrations of the vibrating device 32, the elastic holder 30 being designed such that the vibrating device 32
• REPLACEMENT LEAF can vibrate the vibrating box 29 regardless of the movements of the washing box 15.
• the lifting element 10, the vibrating device 32, the washing pulsator 35 and the conveying pulsator 40 can all be actuated remotely or even under program control according to the requirements of the material to be processed.
• Optimal cleaning of the items to be cleaned or optimum washing and conveying performance can be achieved in that the amplitude and the frequency of the drive cylinders can be set independently of one another. This can take place during operation, that is to say without the cleaning machine 1 being temporarily stopped.
• vibration devices 45 and 46 are provided on the underside of the wash box floor 18 in the region of the center of gravity of the wash box 15, the vibration device 45 being assigned to the first partial floor 19 and the other vibrating device 46 to the second partial floor 20.
• These vibrating devices 45 and 46 are designed in such a way that they can exert forces directed vertically onto the partial bottoms 19 and 20, and can thereby also set the washing box 15 into an oscillating movement.
• the vibration devices 45 and 46 are also advantageously designed as pressure-actuated drive cylinders and can be operated as an alternative to the washing pulsator 35 or delivery pulsator 40 or simultaneously with these.
• washing pulsator 35 or delivery pulsator 40 and the vibrating devices 32, 45 and 46 are described in detail below.
• FIG. 3 shows a longitudinal section of a drive cylinder which is used as a washing pulsator 35 or delivery pulsator 40 in the cleaning machine 1.
• This drive cylinder 47 consists essentially of a control magnet arrangement 48, a control valve 49, and a cylinder housing 50 surrounding the control valve 49 with a drive piston 51, and a damper member 52 with a piston rod 53.
• the control magnet arrangement 48 has a stator 58 inserted into an axial opening 54 of one end face 55 of the cylinder housing 50 consisting of two housing halves 56 and 57, in which an armature 59 is displaceably mounted in the longitudinal direction.
• the end of the armature 59 facing the control valve 49 is connected to a valve body 60, which is also accommodated in a valve housing 61 so as to be displaceable in the longitudinal direction.
• This valve housing 61 is held in the drive piston 51 by means of a locking ring 62.
• the drive piston 51 is, in turn, received in a longitudinally displaceable manner in the housing of the drive cylinder 47 and, at its end 63 facing away from the control magnet arrangement 48, has the transmission element designed as a damper element 52, which moves axially from a damper housing 64 and one in the latter ⁇ Lich guided damper piston 65.
• the damper piston 65 is finally connected to the piston rod 53, which acts as a piston rod 39 or 44 on the wash box floor 18.
• FIG. 4 shows a longitudinal section through one of the vibration devices 32, 45 or 46. These vibration devices 32, 45 or 46
• REPLACEMENT BLUE are designed in the same way as the washing pulsator 35 or the delivery pulsator 40 as a pressure medium-actuated drive cylinder 66 and essentially consist of a control magnet arrangement 67 corresponding to the control magnet arrangement 48, a control valve 68 corresponding to the control valve 49 and a cylinder housing 69 surrounding the control valve 68 Drive piston 70 and a vibrating mass 71 axially connected to the driving piston 70.
• the vibrating mass 71 is accommodated coaxially in a housing extension 72 of the housing 69 and is axially movable therein, coupled to the drive piston 70 in the housing space 74.
• This vibration projection 71 is attached to an axial pin 75 of the drive piston 70 and is screwed to the drive piston 70 with a tension bolt 76.
• an axial channel 77 is provided, which allows the hydraulic medium located in the housing space 74 to flow from one space section 78 into the other space section 79.
• the structure of the control magnet arrangement 48 and 67 of FIGS. 3 and 4 shown in an enlarged representation in FIG. 5 is described in detail below.
• the stator 58 inserted into the individual housing half 56 has a pole shoe 81 formed as an end wall 80 and integrally connected to the stator 58, whereas the other end wall of the stator 58 is formed by a pole shoe 83 inserted into an inner groove 82.
• These pole pieces 81 and 83 have bearings 84 and 85, in which axial extensions 86 and 87 of armature 59 are mounted so as to be longitudinally displaceable.
• These axial extensions 86 and 87 can either be integrally formed on the armature 59, but they can also be formed as separate components that can be connected to the armature 59.
• the armature 59 has recesses 88 which are introduced, for example in the form of axial bores in the end walls 89 and 90, at a radial distance from the axis 91 of the armature 59 and at the same distance from one another.
• These recesses 88 serve as receptacles for return springs 92, which in turn are supported on the bottom of the recesses 88 and on the inner surfaces of the pole shoes 81 and 83.
• the stator 58 consists essentially of a cross-sectionally T-shaped inner ring 93 which is fitted into the recess 94 of the housing of the stator 58.
• the inner ring 93 consists of a sleeve 97, which forms two legs 95 and 96 and is coaxial with the housing of the stator 58 and is connected to the housing of the stator 58 via an annular web 98.
• Control windings 99 and 100 of a coil former 101 are provided on both sides of the web 98 between the sleeve 97 and the housing of the stator 58.
• control windings 99 and 100 facing away from the web 98 lie against the pole shoes 81 and 83 and are partially under-gripped by projections 102 and 103 of the pole shoes 81 and 83 projecting axially in the direction of the legs 95 and 96.
• the control windings 99 and 100 are therefore apart from the areas 104 and 105 of the legs 95 and 96, the web 98, a part of the housing of the stator 58, a part of the pole pieces 81 and 83 and the axial projections 102 and 103 embraced.
• the armature 59 is designed such that it lies with little play in the sleeve 97 between the axial end faces 106 and 107 of the projections 102 and 102 in the stator 58.
• the length of the body of the armature 59 therefore corresponds to the distance between the two axial end faces 106 and 107 of the projections 102 and 103.
• the axial extension 97 of the armature 59 is designed as a connecting element 108, which is motionally coupled to the valve body 60 via a coupling 109.
• This coupling 109 is designed as a bracket 111 enclosing a terminal attachment 110 of the valve body 60, the attachment 110 being received in the bracket 111 with axial and radial play.
• a defined end position of the extension 110 in the bracket 111 is achieved by means of springs 112 which urge the extension 110 into a defined rest position.
• the housing of the stator 58 has a control current connection 113 for a power supply to the control windings 99 and 100. At the end, the housing of the stator 58 is closed by means of a locking element 114.
• valve body connected to the connecting element 108 of the armature 59 via the coupling 109 60 essentially consists of a slide 115 and two sealing pistons 116 and 117, each of which are at a certain distance from one another and are axially displaceable in a sealing manner in a bore 118 of the valve housing 61 by means of the valve body 60.
• the valve housing 61 has annular grooves 119, 120 and 121 formed in the circumferential surface of the bore 118, which are connected via bores 122, 123 and 124 to circumferential grooves 125 and 126 provided in the circumferential surface of the valve housing 61. These circumferential grooves 125 and 126, as well as the bore 123 communicate with ring grooves 127, 129 and 128, which are provided in the inner circumferential surface of the drive piston 51.
• the annular groove 127 is connected via a bore 130 to the inlet opening 131 and the annular groove 129 via the bore 132 to the outlet opening 133.
• the annular groove 128 is connected via a bore 134 to a first annular channel 135, which is provided between the first housing half 56 and the drive piston 51.
• a second ring channel 136 and a third ring channel 137 are provided between the first housing half 56 and the drive piston 51 and between the second housing half 57 and the drive piston 51.
• the outer surface of the drive piston has a shoulder 138 from a radius R1 to a radius R2 in the area of the first ring channel 135, and a shoulder 139 from a radius R2 to a radius R3 in the area of the second ring channel 136.
• These shoulders 138 and 139 form drive surfaces representing annular surfaces 140 and 141, on which the pressure medium flowing in via the inlet opening 131 can act on the drive piston 51.
• the relationship R2>R3> R1 applies to the radii R1, R2 and R3. Accordingly, the ring area 140 has a larger area than the ring area 141, the ring area 141 preferably being half the size of
• a sealing connection between the first housing half 56 and the second housing half 57 is achieved via a sealing ring 142 which is provided in the seat of the housing half 57 for the housing half 56. Furthermore are
• REPLACEMENT LEAF further sealing rings 143 are provided on the circumference of the valve housing 61 between the end face facing the armature 59 and the circumferential groove 125, between the circumferential groove 125 and the bore 123 and between the bore 123 and the circumferential groove 126, which prevent overflow of the hydraulic medium. Furthermore, a sealing closure of the ring groove 120 is achieved in that the slider 115 is formed with a width that corresponds exactly to the width of the ring groove 120, possibly only with a minimally larger width.
• the damper member 52 is described with reference to the representation of the longitudinal section through the drive cylinder 47 shown in FIG. 3.
• the damper housing 64 of the damper member 52 is rigidly connected by means of at least one screw 144 to the end face of the drive piston 51 facing away from the control magnet arrangement 48.
• the damper piston 65 is movably received in the longitudinal direction in the cylinder bore 145 of the damper housing 64 and axially guided by means of coaxial pins 146 and 147, which are mounted in bearings 148 and 149 provided in the end faces of the damper housing 64.
• the bearing 149 is provided coaxially in a screw cap 150, the screw cap 150 also additionally having a hydraulic seal 151 and a dust protection seal 152 through which the coaxial pin 147 is guided.
• the damper housing 64 has a connecting bore 154, which connects the first damper space 157 to the outlet opening 133 via a transverse bore 155 and a check valve receiving space 156, via the third ring channel 137.
• the second damper chamber 158 is via a second check valve receiving chamber 159
• gBSATZBLT * also connected to the third ring channel 137 and thus the outlet opening 133.
• Both check valve receiving spaces 156 and 159 have check valves 160 which prevent the hydraulic medium from flowing out of the two damper spaces 157 and 158.
• the two damper chambers 157 and 158 are connected to one another via a throttle bore 161 provided in the damper piston 80, via which hydraulic medium can flow from the first damper chamber 157 into the second damper chamber 158 or vice versa.
• seals in the form of a shaft sealing ring 163 and a dust protection seal 164 are provided on the end face 162 of the second housing half 57 facing away from the control magnet arrangement 48, between which the damper housing 64 is received and which prevents the hydraulic medium from escaping and becoming contaminated prevent third ring channel 137.
• any existing magnetization of the magnetizable material e.g. made of soft iron, existing armature 59 and the inner ring 93, which also consists of a magnetizable material, with web 98 and
• REPLACEMENT B L ATT Sleeve 97 and the jacket of the stator 58 and the pole pieces 81 and 83 are still unordered, that is to say statistically oriented.
• the control magnet arrangement 48 or 67 is started up, the two control windings 99 and 100 of the coil former 101 are first excited with a quiescent current. This takes place in that a constant, low control current is applied to the control current connection 113, which is connected to a control current source (not shown), through which both control windings 99 and 100 flow.
• This control current generates a magnetic field around each of the control windings 99 and 100, the two fields each having opposite directions, via these fields the magnetization of the soft iron of the stator 58, the armature 59 and the pole pieces 81 and 83 is oriented, which is a needed some time. If the magnetization is finally aligned in the direction of the field lines, the control magnet arrangement 48 or 67 is ready for operation.
• the armature 59 is in its rest position even with such a energized coil body 101, since the indu ⁇ through the two fields of 91 and 100 Steuerwick ⁇ isme ed magnetic forces on the armature "59 aus ⁇ same and the armature 59 continues from the remind ⁇ is held in the rest position 92.
• This position of the armature 59 in the stator 58 is stable since the forces of the return springs 92 and the magnetic forces which result from energizing the control windings 99 and 100 of the coil body 101 are balanced.
• the end wall 89 moves in the direction of the projection 102 in such a way that the end wall-side circumferential surface of the armature 59 is overlapped by the projection 102.
• the end wall 90 of the armature 59 moves away from the projection 103 of the pole piece 83 to the extent that the end wall 89 approaches the pole piece 81.
• the magnetic resistance for the magnetic flux at the transition from the armature 59 to the projection 102 is reduced on the one hand, and on the other hand the magnetic resistance for the magnetic flux at the transition from the armature 59 to the projection 103 is increased.
• This circumstance also causes an increase in the magnetic force of the coil body 101 on the armature 59 in the direction of the pole shoe : 81.
• the delay caused by the self-inductance L is relatively small compared to the time that would be required for a complete orientation of the magnetization. Accordingly, the armature 59 follows a change in the control current with only a slight time delay, which is approximately 1-2 ms.
• the armature 59 is axially displaced in the direction of the pole piece 81 via the magnetic force of the coil former 101, its end wall 89 comes to rest on the inner surface of the pole piece 81.
• the armature 59 is later detached from the inner wall of the pole piece 81 can facilitate, the end wall 89 or the inside of the pole piece 81 with a magnetic insulator, for example Plastic, aluminum or the like may be provided.
• the valve body 60 in the valve housing 61 is also displaced via the connecting element 108 and the coupling 109.
• the slide 115 moves in the direction of the control magnet arrangement 48 or 67 and thereby connects the annular groove 120 to the annular groove 121. Since the annular groove 121 via the bore 124, the circumferential groove 126, the annular groove 129 and the bore 132 is connected to the third annular channel 137 and thus to the outlet opening 133 connected to the tank T, the hydraulic medium located therein is depressurized. Thus there is also ambient pressure in the annular groove 120, in the bore 123, in the annular groove 128, in the bore 134 and thus in the first annular channel 135.
• the inlet opening 131 is connected to a pressure supply unit, for example a pump P, there is in the second annular channel 136, in the bore 130, in the annular groove 127, in the circumferential groove 125, in the bore 122 and in the annular groove 119 the high or working pressure of the pump P, which can have a value of up to 300 bar. Since the end faces of the sealing piston 116 and the slide 115 facing the annular groove 119 have the same sizes, the pressure prevailing in the annular groove 119 does not cause any displacement of the valve body 60.
• a pressure supply unit for example a pump P
• the drive piston 51 or 70 experiences a force displacing it in the direction of the control magnet arrangement 48 or 67.
• This displacement of the drive piston 51 b. 70 causes a displacement of the Ven _-_ igephases 61, since this is firmly connected to the drive piston 51 and 70 via the locking ring 62.
• the valve housing 61 is also displaced in the direction of the control magnet arrangement 48 and 67, the annular groove 120 and the annular groove 121 are separated from one another again, since the displacement of the valve housing 61 causes the valve body 60 to be inserted.
• valve body 60 In the end, if the valve body 60 is displaced in the direction of the control magnet arrangement 48 or 67 when the control magnet arrangement 48 or 67 is actuated, the drive piston 51 or 70 is also tracked in the direction of the control magnet arrangement 48 or 67 causes until the drive piston 51 and 70 and with it the valve housing 61 is brought into a position in which the slide 115 closes the annular groove 120 again.
• This position of valve body 60 and valve housing 61 again corresponds to the basic position shown in FIGS. 3, 4 and 6.
• the armature 59 can be deflected from this first working position, for example, by the following four options:
• the current for the control winding 99 is brief, i.e. interrupted for a period of 1-2 ms and then again takes on the value in the amount of the quiescent current, whereas the control winding 100 is constantly supplied with the quiescent current,
• the current of the control winding 99 is temporarily, i.e. reduced to a value below the quiescent current for a period of 1-2 ms and then again assumes the value for the quiescent current, whereas the control winding 100 is continuously supplied with the quiescent current.
• the current for the control winding 99 maintains its value which is above the quiescent current, whereas the current of the control winding 100 is briefly increased to a value which is above the value of the current of the control winding 99 and finally both currents are reduced to the value of the quiescent current.
• the armature 59 is deflected from its working position in the direction of the basic position and held there by means of the spring force of the return springs 92. This deflection from the working position back into the base can also take place within a very short time, since the magnetization in the stator 58, in the armature 59 and in the pole pieces 81 and 83 does not have to be reoriented, but only the self-inductance L of the control winding 99 and / or counteracts the control winding 100.
• the time delay of the displacement of the armature 59 compared to the time at which the control winding 99 and / or the control winding 100 are supplied with the changed control current is in the range of 1-2 ms. From this rest position, the armature 59 can be pushed back into the first working position or else into the second working position in the direction of the pole shoe 83. For this purpose, the current for the control winding 100 is corresponding to the value of the working
• REPLACEMENT LEAF Increase current so that the magnetic force of the coil body 101 in the direction of the pole piece 83 is increased.
• the armature 59 now moves from the rest position, for example into the second working position, the end wall 90 shifting in the direction of the pole piece 83 such that the peripheral edge of the armature 59 is partially covered by the projection 103.
• the opposite end wall 89 of the armature 74 moves away from the projection 102 of the pole piece 81. This increases the magnetic resistance for the flow around the control winding 99 in the region of the projection 102 and the end wall 89, whereas the magnetic resistance for the Flow around the control winding 100 in the area of the projection 103 and the end wall 90 is reduced by the overlap of the projection 103 and armature 59, so that the armature 59 is additionally accelerated in the direction of the pole piece 83.
• magnetic insulators can be provided on the end wall 90 of the armature 59 and / or on the inner surface of the pole shoe 83, which facilitate a later displacement of the armature 59 from the second working position back to the rest position in that no too low magnetic resistance between the End face 90 of the armature 59 and the pole shoe 83, for example by direct contact.
• REPLACEMENT LEAF A movement of the armature 59 in the stator 58 from the first working position back to the rest position causes the valve body 60 in the valve housing 61 to be displaced in the direction of the damper member 52 or the vibration mass 71.
• the slide 115 is displaced in this way in the valve housing 61 that the annular groove 120 is connected to the annular groove 119.
• the drive piston 51 or 70 is displaced together with the damper member 52 or the vibration mass due to the resulting force acting on the two annular surfaces 140 and 141. 71 to the right.
• the drive piston 51 or 70 thus follows the movement of the valve body 60 until the annular groove 120 is pushed over the slide 115 again and the annular groove 120 is thereby separated from the annular groove 119. This position again corresponds to the basic position or rest position of the control valve 49 or 68 shown in FIGS. 3, 4 and 6.
• valve body 60 in the valve housing 61 When the valve body 60 in the valve housing 61 is reset in the direction of the control magnet arrangement 48 or 67, the slide 115 moves out of its basic position in such a way that it connects the annular grooves 120 and 121 again.
• this displacement of the valve body 60 of the drive pistons 51 and 70 follows due to the working or high pressure of the pressure supply unit, namely the pump P, prevailing on the annular surface 141 of the shoulder 139 of the second annular channel 136 forming the drive surface 51 and 70 and thus the valve housing 61 is shifted until the annular groove 120 is pushed over the slide 115 again and the annular grooves 120 and 121 are separated from one another again.
• the quiescent current of one of the two control windings 99 or 100 has an alternating current of e.g. 50 Hertz superimposed, the amplitude of which is less than the quiescent current
• the armature 59 can be moved back and forth with the frequency of the alternating current between its first and second working positions, so that the drive pistons 51 and 70 alternate depending on this frequency is moved back and forth between two end positions, which represent two flow positions I and II for the control valve 49 and 68, respectively.
• a pulsating direct current e.g. is generated by full-wave rectification, the quiescent current
• REPLACEMENT LEAF be overlaid. It can further be provided that one of the control windings 99 or 100 is only supplied with a pulsating direct current.
• the hydraulic medium has enough time to flow from one damper chamber 157 into the second damper chamber 158 via the throttle bore 161, so that the damper housing 64 can move relative to the damper piston 65.
• the attenuator 52 is therefore hard at high frequencies and soft at low frequencies.
• This property of the damper member 52 is used in the cleaning machine 1 according to the invention in such a way that the height position of the washing box 15 can adjust to an equilibrium position when filling with the items to be cleaned and cleaning liquid by compressing the vertical springs 16, with those in the rest position
• Drive cylinders -47 and 66 of the damper piston 65 in the damper housing 64 shifts due to a change in position of the washing box 15. If the washing box 15 is in an equilibrium position, the damper piston 65 is also in a corresponding position in the damper housing 64 without a static force being present in the damper member 52. That is, the position of the damper piston 65 adjusts to the height of the wash box 15. If the drive cylinders 47 and 66 are now operated, the oscillating movements of the damper housing 64 are transmitted to the damper pistons 65 and from there to the wash box 15 almost without damping.
• the two pulsators 35 and 40 can execute oscillating movements, for example by exciting the control magnet arrangement 48 with an alternating current, the movements
• REPLACEMENT LEAF of the two drive cylinders 47 can either be in phase or out of phase and can take place with the same amplitude or with different amplitudes. If only the washing pulsator 35 is operated, it performs an oscillating movement, so that the washing box 15 is only pivoted essentially about the left pivot axis 4. In contrast, the wash box 15 pivots about the right pivot axis when only the delivery pulsator 40 is operated and the wash pulsator 35 is at rest. This makes it possible to move the washing box 15 in such a way that the transport speed of the items to be cleaned which are in the cleaning liquid can be precisely controlled. In this way, it is possible to optimally adapt to the item currently to be cleaned.
• This adjustment can be carried out both during operation and when the cleaning machine 1 is at rest.
• any desired self-contained movement can be generated by phase shift and different amplitudes, so that the material to be cleaned both in the conveying direction, ie in the direction of the discharge opening 26 and can be conveyed against this direction at almost any speed.
• This phase and amplitude control is advantageously effected by means of a control current device, not shown, which controls the control magnet arrangements 48 of the two pulsators 35 and 40 with working currents of different currents.
• the trajectories of the washing box 15 can be controlled accordingly on a straight as well as on an elliptical or circular path.
• the washing box 15 In addition to driving the washing box 15 by means of the washing pulsator 35 and the conveying pulsator 40, the latter can also be driven by the vibration devices 45 and 46.
• These Vibrationseinrich ⁇ lines 45 and 46 are designed as a simple mass vibrator and perform perpendicular to the partial floors 19 and 20 vibrations, so that the wash basin 15 can also be set in vibration by the vibrating devices 45 and 46.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Reciprocating, Oscillating Or Vibrating Motors (AREA)

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Citations (5)

• 1989
  • 1989-10-13 DE DE19893934296 patent/DE3934296A1/de active Granted
• 1990
  • 1990-10-12 WO PCT/EP1990/001727 patent/WO1991005610A1/de unknown

Patent Citations (5)

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