EP4192626A1

EP4192626A1 - System for treating mass-produced parts, said system having an auxiliary drive device

Info

Publication number: EP4192626A1
Application number: EP21737465.1A
Authority: EP
Inventors: Martin Müller; Hubert Jongen; Gregor Beckmann
Original assignee: Wmv Apparatebau GmbH
Current assignee: Wmv Apparatebau GmbH
Priority date: 2020-08-06
Filing date: 2021-06-30
Publication date: 2023-06-14
Also published as: WO2022028782A1; EP3950142A1; US20230286011A1

Abstract

The invention relates to a system for treating mass-produced parts, said system comprising: a support structure (2) with a support element (8); a basket support (5) for at least two centrifuge baskets (1); a main drive device (7), which is fastened to the support structure (2) and has a main drive (9) and a longitudinal shaft (6), the longitudinal shaft (6) being mounted rotatably about a main axis (A) in relation to the support element (8) and being driveable in rotation about the main axis (A) by the main drive (9), the basket support (5) being held in suspended fashion on the longitudinal shaft (6) and being connected to the longitudinal shaft (6) for conjoint rotation; and an auxiliary drive device (17) with at least one motor (18) and, for each centrifuge basket (1), a force-transmission portion (19) for rotating the centrifuge basket (1) about a basket axis (K) radially distanced from the main axis (A), the at least one motor (18) of the auxiliary drive device (18) being arranged on the basket support (5).

Description

Plant for treating mass-produced parts with an auxiliary drive device

description

The invention relates to a system for treating mass-produced parts, the system comprising: a support structure with a support element, a basket carrier for at least two centrifuge baskets, a main drive device fastened to the support structure and having a main drive and a longitudinal shaft, the longitudinal shaft rotating about a main axis relative to the support element rotatably mounted and can be driven to rotate about the main axis by the main drive, the basket carrier being held hanging on the longitudinal shaft and having a base body connected in a rotationally fixed manner to the longitudinal shaft, and an auxiliary drive device with at least one motor and, for each centrifuge basket, a power transmission line for rotating the centrifuge basket by one basket axis radially spaced from the main axis.

Plants of this type can be used for treating, for example for coating, mass-produced parts in particular that can be poured, such as screws, stamped parts or the like. After the mass parts have been poured into the centrifuge baskets, they are immersed in an immersion bath with a liquid coating agent to wet the mass parts and can be rotated around the basket axes if necessary. The centrifuge baskets are then spun outside of the coating material in order to sling excess coating material off the mass parts.

ES 2 204 214 A1 discloses a system for treating mass-produced parts accommodated in centrifuge baskets, which can be successively transferred to three stations by means of a rotary arm suspended from a frame. For this purpose, a basket arrangement made up of three of the centrifuge baskets is arranged on both longitudinal ends of the rotary arm, each of which has a basket shaft at the respective longitudinal end of the Rotating arm are rotatably held. The three stations are arranged around an axis of rotation of the rotary arm, so that the basket assemblies can be transferred from one station to the next station by rotating the rotary arm in steps. In the filling station, the centrifuge baskets of the respective basket arrangement are filled with mass-produced parts one after the other. For this purpose, a rotary motor located on the end of the basket shaft rotates the respective basket arrangement step by step around the basket axis in order to successively fill the mass parts into the three centrifuge baskets via a chute. This is followed by the treatment station, in which case the basket arrangement is raised into a dip tank by means of a lifting device in order to dip it. In the treatment station, the centrifuge baskets of the respective basket arrangement are rotated about the basket axis by means of a separate centrifuge motor in order to sling off excess treatment liquid from the mass parts after the immersion tank has been lowered. Finally, the unloading station follows, in which the centrifuge baskets of the respective basket arrangement are unloaded one after the other via a conveyor belt. For this purpose, the rotary motor rotates the respective basket arrangement step by step around the respective basket axis, so that the centrifuge baskets can be aligned one after the other over the conveyor belt and unloaded. It is considered disadvantageous that the system is complex and expensive to manufacture and maintain due to the large number of motors and that the excess treatment liquid can only be thrown off moderately by rotating the basket arrangements about the basket axes.

Another system for treating mass-produced parts is known from EP 3 441 149 A1. The system has a basket carrier with which two centrifuge baskets are reversibly detachably connected. The basket carrier is suspended from a longitudinal shaft, the longitudinal shaft being mounted so as to be rotatable about a main axis relative to a central beam of the frame. The longitudinal shaft is drive-connected to a main motor attached to the central beam, so that the basket carrier, which is non-rotatably connected to the longitudinal shaft, can be driven by the main motor to rotate about the main axis. In order to be able to additionally rotate the centrifuge baskets about their basket axles, which are spaced radially from the main axis, drive wheels, which are driven by toothed belts, should be arranged on the ends of the basket axles facing the central beam. The toothed belts are to be driven by a gear wheel arranged on the longitudinal shaft so that it can rotate relative to it, the gear wheel arranged on the longitudinal shaft in turn being connected via another toothed belt with a pinion of one on the central beam of the Scaffold arranged auxiliary motor to be driven. Due to the high centrifugal forces that occur during operation of the system, it has proven useful to attach not only the main motor but also the secondary motor for rotating the centrifuge baskets to the stationary frame. However, it is considered disadvantageous that a power transmission from the auxiliary motor to the belt drives arranged on the basket carrier is structurally complex and appears to be maintenance-intensive.

Another system for treating mass-produced parts is known from KR 10-2016-0069654 A, in which the motors of the auxiliary drive device are arranged on the basket carrier. The basket carrier is rotatably suspended about an axis of rotation on a frame on which a main motor for driving the basket carrier in rotation is arranged. The motors of an auxiliary drive device are arranged on radially outer end faces of the basket carrier, with a power transmission unit being provided between the motors and rotary shafts. Another system for treating mass-produced parts is known from KR 10-2016-0025770 A.

An object of the invention is to improve the prior art plant.

The object is achieved by a system of the type mentioned in which the auxiliary drive device is arranged on the basket carrier. Advantageous embodiments result from the dependent claims.

It is advantageous that the at least one motor is arranged directly on the basket carrier. This eliminates the need for mechanically complex and fault-prone connections in order to rotate the centrifuge baskets about the basket axes with a drive arranged on the support structure. Instead, the at least one motor always rotates together with the basket carrier about the main axis when the main drive device drives the basket carrier in rotation. This provides a system whose power take-off device is more compact and withstands the centrifugal forces better. The main drive device and the auxiliary drive device are mechanically separated from one another, so that both drive devices can work independently of one another. The power take-off device is preferably arranged on the basket carrier. The auxiliary drive device then always rotates with the basket carrier about the main axis when the basket carrier is driven in rotation by the main drive. As a result, the power take-off device arranged on the basket carrier is spatially spaced apart from the supporting structure, as a result of which the system as a whole is easier to manufacture and easier to maintain.

The basket carrier is preferably only connected to the longitudinal shaft, or fastened to it. In other words, the basket carrier is attached to the longitudinal shaft in a freely hanging manner. The basket carrier is preferably aligned horizontally and can also be referred to as a rotor.

The longitudinal shaft can be designed as a hollow cylinder or as a hollow shaft, through which supply lines for connecting the power take-off device to a supply system of the installation are routed from the supporting structure to the basket carrier. The at least one motor can be an electric motor, in particular a servomotor. The supply system can include an electrical power supply for the system, to which the at least one motor can be connected. In principle, however, it is also possible for the at least one motor to be a pneumatic motor. Accordingly, the supply system can include a pneumatic ring line of the system in order to be able to operate the at least one motor with compressed air. The supply lines can thus include electrical lines and/or pneumatic lines. In this way, the power take-off device and optionally other components arranged on the basket carrier can be connected to an electrical power supply and/or a pneumatic supply system of the installation. Of course, the electrical power supply for the power take-off device can also be provided via a power storage device for electrical energy, which can also be attached to the basket carrier. As a result, the auxiliary drive device can be self-sufficient from a central power supply of the system, to which the main drive device can be connected. Thus, the longitudinal shaft can in principle also be a solid shaft, especially in the case of the self-sufficient option described above.

Furthermore, a control line or a bus be guided. Sensors, actuators and the like arranged on the basket carrier for the auxiliary drive device and for optionally further components arranged on the basket carrier can thus be integrated into a bus system of the plant, for example. In this way, for example, the rotational position of the basket carrier or the centrifuge baskets, directions and speeds of rotation, the status of the connection arrangement, or whether the centrifuge baskets are coupled or uncoupled, etc. can be individually queried and controlled.

A central rotary feedthrough for the supply lines, in particular the electrical lines and/or pneumatic lines and optionally available control lines, can be arranged at an end of the longitudinal shaft facing away from the basket carrier, with the central rotary feedthrough having a first body supported relative to the supporting structure and a first body connected in a rotationally fixed manner to the longitudinal shaft second body may have. The rotary feedthrough allows the lines to pass between the stationary first body and the rotating second body. The lines coming from the support structure can thus be routed reliably through the central rotary feedthrough into the end of the longitudinal shaft facing away from the basket carrier, through the longitudinal shaft, out again at an end of the longitudinal shaft facing the basket carrier and finally to the basket carrier.

The basket carrier can comprise a base body. A shaft-hub connection, for example with a key and lock nut, can be used to fasten the base body to the longitudinal shaft. For this purpose, the base body can have a central receptacle into which an end of the longitudinal shaft facing the basket carrier can be inserted. Alternatives to the feather key connection are possible in principle, with the connection preferably holding the base body firmly on the longitudinal shaft not only rotationally but also translationally due to its suspended arrangement. For example, the base body could be pressed onto the longitudinal shaft.

A rotating platform can be arranged on the basket carrier, in particular the main body of the basket carrier, for each centrifuge basket, the rotating platforms being drivable in rotation about the basket axes by the auxiliary drive device. Thus, the rotary platforms can each be drive-connected to one of the power transmission lines being. The at least one motor is drive-connected to the respective power transmission train. The rotary platforms can be flange-like in design or can include flanges. The rotary platforms can be arranged on or below an underside of the base body that faces away from the support element.

For the reversibly detachable connection of the centrifuge baskets to the basket carrier, connection arrangements can be provided which have components on the rotary platforms and other components on the centrifuge baskets. In particular, first connectors of the connection arrangements can be arranged on the rotary platforms and second connectors of the connection arrangements, which can be connected to the first connectors, can be arranged on the centrifuge baskets. Preferably, the second connectors are passive connectors that can be inserted into the active, first connectors. Passive connectors are rigid components that are held in the connected state by the active connectors. This means that the centrifuge baskets can also be sandblasted, for example, without having to fear damage to the second connector. When arranging the first connectors on the rotary platforms, it is also advantageous that the active connection partners of the connection arrangements can be connected to a supply network of the system via the basket carrier.

The base body of the basket carrier can have through bores which are concentric to the basket axes and through which pneumatic lines for actuating the first connector are routed from the base body to the rotary platforms. The first connectors can be actuated with compressed air via the pneumatic lines. In principle, however, hydraulic or electrical lines for actuating the first connector would also be possible. The in particular pneumatic lines are preferably routed together with the electrical lines through the longitudinal shaft and the central rotary leadthrough to the supporting structure in order to be able to connect the first connector to a central compressed air supply of the system. The electrical lines and/or the control lines can be routed to the first connectors in order to be able to supply them with electrical power if required and/or to be able to connect them to the control unit. A secondary rotary feedthrough for the lines for actuating the first connector can be arranged on the basket carrier for each rotary platform, with the secondary rotary feedthroughs each having a first secondary body supported against the base body and a first secondary body non-rotatably connected to the rotary platform have associated second secondary body.

The first connectors can be pneumatic clamping modules or centering clamps, in which the second connectors designed as connecting bolts can be clamped. The first connectors can each have a base body with a bolt receptacle into which the connecting bolt can be inserted. When the connecting bolt is inserted, it can be clamped with a locking mechanism on the base body. In this connected state, the connector units absorb the centrifugal forces generated by the rotating centrifuge baskets during operation of the system. In this way, in the connected state, the torque applied by the drive devices during operation of the system can be reliably transmitted to the centrifuge baskets via the connection arrangements. It is advantageous that only an axial movement of the centrifuge baskets and the basket carrier relative to one another is necessary to insert the connecting bolts into the clamping modules.

The locking mechanisms can each have form-fitting elements, which are arranged displaceably on the base body of the first connector. The form-fitting elements can each be displaceable parallel to a plane which is aligned transversely, in particular perpendicularly, to the main axis. The form-fitting elements can preferably be displaced transversely, in particular radially, to a central axis of the respective base body. To fix the connecting bolts inserted into the bolt receptacles, the positive-locking elements can be shifted towards the central axis of the respective base body. It is advantageous that only the locking mechanisms, in particular the form-fitting elements, have to be moved in order to lock the inserted connecting bolts in the clamping modules. A rotary movement of the centrifuge baskets and the basket carrier relative to one another, as is necessary with a bayonet closure, for example, does not take place. The positive-locking elements can be locking bolts that are displaceably arranged on the base bodies. Preferably, two of the form-fitting elements, in particular the locking bolt, are displaceably arranged on each of the base bodies and are arranged diametrically opposite one another. The locking mechanisms can include springs which apply spring force to the form-fitting elements in a locked position, ie towards the central axis of the respective base body. Thereby are the connector units are clamped without pressure. The release process of the locking mechanisms can take place pneumatically or, in principle, also hydraulically. As an alternative to being designed as a locking bolt, the positive-locking elements can also be displaceable balls. As a result, the connector units create a secure connection that keeps the connected centrifuge baskets securely on the basket carrier even in the event of disruptions in the operation of the system, for example caused by a failure of the electrical power supply or a failure of pneumatic or hydraulic systems.

In particular, the connecting bolts can each have a groove running around a bolt axis, in which the form-fitting elements engage in a form-fitting manner in the connected state. As a result, in the connected state, the connecting bolts are fixed at least largely without play in the bolt receptacles of the base bodies, axially and radially with respect to the respective central axis. The bolt axes run parallel to the main axis, at least when the centrifuge baskets are connected to the basket support.

In order to turn the rotary platforms around the basket axes, the auxiliary drive device can have several of the at least one motor. In particular, the auxiliary drive device can have its own motor for each power transmission train. In this way, the power transmission lines can be driven independently of one another. In other words, the power take-off device can have its own drive train for each rotating platform, consisting of a motor and a power transmission train, in order to be able to drive the assigned rotating platform rotating about the basket axis. As a result, the centrifuge baskets can be rotated individually or together. Likewise, the centrifuge baskets or the rotary platforms can be driven to rotate in opposite directions or in the same direction in relation to the direction of rotation and to rotate at the same speed or at different speeds in relation to the rotational speed. Due to the fact that the auxiliary drive device works independently of the main drive device, the rotational movements of the basket carrier around the main axis and the rotational movements of the rotary platforms or the centrifuge baskets around the basket axes are independent of one another. In principle, however, the power take-off device can also have only a single motor points, which drives the power transmission lines centrally. The motors can be arranged symmetrically to the main axis on the basket carrier in order to avoid imbalances when the basket carrier rotates about the main axis.

The at least one motor can include a rotor shaft that can be driven in rotation about a rotor axis, wherein the rotor axis can be arranged on an imaginary first circle and the basket axes can be arranged on an imaginary second circle. The first circle and the second circle can be arranged concentrically to the main axis, wherein a first radius of the first circle can be smaller than a second radius of the second circle. As a result, the centrifugal forces acting on the at least one motor during rotation of the basket carrier about the main axis, at which speeds of up to approximately 200 revolutions per minute are possible, can be reduced to a minimum due to the installation space of the at least one motor. In particular, the first radius can be less than 0.5 times the second radius. Furthermore, the rotor axis can be arranged at a distance of less than 300 millimeters from the main axis. In particular, the distance between an axis of rotation about which the rotor shaft of the at least one motor rotates in a drivable manner and the main axis can be less than 200 millimeters.

In particular, the power transmission strands can each have a belt drive. In this way, the at least one motor can be spaced apart from the respective basket axis and advantageously positioned in the direction towards the main axis on the basket carrier. This increases the service life of the at least one motor, making the system overall more robust and easier to maintain. The belt drives can have toothed belts, although in principle other types of belts or another traction drive are also possible. However, the toothed belt drives offer the advantage that narrower angles of contact are possible compared to other traction drives, which means that the toothed belts ensure reliable torque transmission despite the high centrifugal forces that occur when the basket carrier rotates about the main axis. In particular, the belt drives each have a drive pulley firmly connected to the rotor shaft of the associated motor and a driven pulley. The driven pulley can be arranged concentrically to the basket axis of the respective power transmission train. Furthermore, the power transmission strands each comprise at least one tensioning device. The respective tensioning device can have a spring mechanism, for example, in order to tension the toothed belt with a tensioning pulley. Likewise, a tensioning device can also be provided, with which the tension of the toothed belt can be set in a fixed manner. In particular, the power transmission strands can each have two of the tensioning devices, for example a spring-loaded tensioning roller and a fixed tensioning roller, with other combinations also being possible.

In order to reduce the drive speed of the engine assigned to the respective power transmission train and to increase the torque accordingly, the belt drive can step down the drive speed. The transmission ratio (abbreviated with "i"), which is defined as the quotient of the speed of the transmission input (here: the drive pulley) and the speed of the transmission output (here: driven pulley), can be in a range of i = 1.5 for the respective belt drive up to i = 10. The axes of rotation of the drive pulleys and driven pulleys are preferably aligned parallel to the main axis. The installation space for the power take-off device on the basket carrier or on the base body of the basket carrier is limited by the dimensions of the basket carrier. However, particularly good results were achieved with a transmission ratio of i=2 to i=6, so that the driven disks, which are larger in diameter, remain within the dimensions specified by the basket carrier, in particular by the base body.

The centrifuge baskets are rotated around the basket axes at up to 15 revolutions per minute when the system is in operation. In order to reduce the drive speed of the at least one motor, which can rotate up to 3000 revolutions per minute for the application here, for example, to the required number of revolutions for the centrifuge baskets, the power transmission lines can each have a reduction gear. The reduction gears can be connected downstream of the belt drive in the power path of the respective power transmission train. The reduction gears can be attached to the basket carrier. Integrating the reduction gear into the respective power transmission train reduces the speed on the one hand and significantly increases the transmissible torque on the other. As a result, the at least one motor of the power take-off device can also have a relatively low nominal torque, making the motor compact can be designed building and can have a low weight. The at least one motor preferably has a nominal torque in the range from 5 Newton meters to 20 Newton meters, and more preferably the nominal torque is at least approximately 10 Newton meters. The nominal torque designates the maximum permissible continuous torque that may act on the rotor shaft of the motor. In particular, the at least one motor can have a maximum rated power of 5000 watts and more preferably at least 2000 watts. Good results in terms of the compact design, the dead weight and sufficient power to be able to rotate the respective centrifuge basket around its basket axis in conjunction with the respective reduction gear were achieved with at least one motor whose nominal power is in the range of 2500 watts and 3800 watts .

The respective power transmission train can have a reduction gear with a gear housing that is attached to the basket carrier, a drive element that can be driven in rotation by the at least one motor, and an output element that is coaxial with the basket axis, with a transmission ratio between an input speed of the drive element and an output speed of the output element is greater than one. The drive element can be an input shaft, for example. The drive element can be rotatably mounted in the transmission housing. The drive element of the respective reduction gear is preferably mounted such that it can rotate about the respective basket axis and can be arranged concentrically to the respective basket axis in the gear housing. The transmission output of the belt drive can be coupled to the transmission input of the reduction gear. For this purpose, the driven pulley of the belt drive can be connected to a drive element of the reduction gear. In particular, the driven pulley can be fixed on the input shaft. It is also possible for one of the at least one motors to drive the drive element directly in rotation, so that no belt drive would be necessary for power transmission. The transmission ratio (abbreviated with "i"), which is defined as the quotient of the input speed, i.e. the speed of the transmission input (here: the input element), and the output speed, i.e. the speed of the transmission output (here: an output element), is for the respective reduction gear is always greater than 1. Preferably, the transmission ratio of the reduction Reduction gears in a range from i=50 to i=200. In particular, the reduction ratio can be between i=90 and i=120. The respective reduction gear expediently has a fixed transmission ratio. Furthermore, the reduction gear or a gear housing of the reduction gear can be arranged concentrically to the respective basket axis.

The respective reduction gear can be an eccentric gear. Due to its axially compact design, this is particularly suitable for use on the basket carrier with the required speed-up ratios. The eccentric gears can be cycloidal gears, for example, in which cam disks transmit torque in a rolling manner. The cycloidal gears do not require gears and are not subject to shearing forces, making them robust and durable. Such a reduction gear is, for example, the TwinSpin reduction gear from the G series from Spinea®. Particularly good results in terms of the reduction ratio and the associated increase in torque and longevity have been achieved, for example, with the reduction gear model TS 335G from the Spinea ® G series. Furthermore, the respective reduction gear can be combined with at least one radial-axial bearing, which can be accommodated in the gear housing. In principle, however, other reduction gears, such as planetary gears or the like, are also possible. The reduction gears can be inserted into the through holes provided concentrically to the basket axes in the base body of the basket carrier and attached to the base body, in particular screwed. The reduction gears can each have a hollow shaft, the lines for actuating the first connector being routed through the hollow shafts.

Furthermore, the rotary platforms can each be attached to the output element of the reduction gear. The entire weight of the rotary platforms and the add-on parts mounted therein, such as connection arrangements, sensors, etc., as well as the centrifuge baskets coupled during operation of the system, preferably bears on the output elements of the reduction gears. In other words, the driven elements can represent the sole connecting element between the rotary platforms and the basket carrier. The rotary platforms may be suspended from the output members and may be synchronous with the output members be driven to rotate around the basket axes. In order to ensure collision-free rotation of the rotary platforms around the basket axes, the respective output element can protrude axially over the edge of the gear housing. In particular, the output elements can protrude axially by about 0.5 millimeters to 5 millimeters and more preferably by about 1 millimeter on an underside of the respective transmission housing. Alternatively, the rotary platforms can also be plate-shaped with a central recessed section that can be attached to the respective output element.

The rotating platforms can each have a central opening. The rotary platforms can protrude in a flange-like manner or radially to the respective basket axis from the output-side end of the reduction gear. The first connectors, sensors and other add-on parts can be arranged in the section of the respective rotating platform that protrudes radially beyond the respective transmission housing. The respective output element can be, for example, a ring gear, an output shaft, an output flange or the like of the reduction gear. The respective output element can be ring-shaped or flange-shaped. The first connectors of the connection arrangements can be arranged on the rotating platforms in order to detachably connect the centrifuge baskets to the rotating platforms or the basket carrier. Because the rotary platforms are suspended from the driven elements, the driven elements hold the centrifuge baskets. So that the reduction gear can safely absorb the axial and radial forces resulting from the operation of the system and, above all, tilting moments, the output elements can be mounted in the gear housings so that they can rotate about the basket axes by means of roller bearings, in particular spherical roller bearings. To this end, it is advantageous if the output elements have the largest possible outer radius. The outer diameter of the output element of the respective reduction gear preferably corresponds to 0.5 times to 1.0 times the outer diameter of the gear housing.

In order to route the lines for actuating the first connector from the base body to the rotary platforms, the input shafts can be designed as hollow shafts. Furthermore, the driven elements can be hollow. In particular, the respective output element can have a hollow-cylindrical output shaft on which the ring gear or the output flange is attached or integrated on the output side. ral is connected. The output shaft can be inserted into the input shaft and mounted so that it can rotate about the respective basket axis relative to it. A needle bearing, for example, can serve as a bearing. Correspondingly, the inner diameter of the input shaft can be larger than the outer diameter of the output shaft. Again, the outside diameter of the output flange can be larger than the outside diameter of the input shaft. Preferably, the outside diameter of the output flange is more than three times the outside diameter of the input shaft and more preferably less than eight times the outside diameter of the input shaft. On the transmission input side, the output shafts can protrude axially out of the input shafts, so that the secondary rotary leadthroughs can be arranged on the protruding ends of the output shafts. In this way, the second bodies of the secondary rotary unions can be connected to the output shafts in a torque-proof manner. As a result, during operation of the system, when the at least one motor drives the power transmission lines, the second bodies of the secondary rotary unions and the rotary platforms are non-rotatably connected by their Connection to the driven elements with the output speed rotating about the respective basket axis.

The system can include at least two centrifuge baskets into which the bulk parts to be treated can be filled, in particular poured. In order to reduce the restoring torques generated by the rotating centrifuge baskets during operation of the system, the centrifuge baskets can be divided into several, in particular two or three, chambers. Compared to a centrifuge basket with only one central chamber, the restoring torques of the centrifuge basket with three chambers are reduced by about 60 percent. In this way, the power take-off device is relieved when rotating the centrifuge baskets around the basket axes. The chambers are spatially separated from each other in the respective centrifuge basket. The walls of the centrifuge baskets can be perforated or provided with holes. An odd number of chambers is preferably provided in order to maximize the total volume of the centrifuge baskets.

In particular, the base body is designed to be rotationally symmetrical to the main axis.

For example, the main body of the basket carrier in the form of a rotary traverse for two of the centrifuge baskets can be designed, with two of the rotary platforms being able to be arranged on the rotary crosshead. Alternatively, the main body of the basket carrier can also be designed in the form of two rotating crossbars for four of the centrifuge baskets arranged in a cross shape with respect to one another, it being possible for two of the rotating platforms to be arranged on each rotating crossbar. Likewise, the main body of the basket carrier can be circular or polygonal in axial view, with two, three, four, five or six of the rotary platforms being able to be arranged on the main body. Preferably, the basket carrier and the secondary drive device arranged on the basket carrier are designed at least as far as possible rotationally symmetrically to the main axis in order to minimize imbalances when the basket carrier rotates about the main axis. The base body preferably rotates in a horizontal plane to which the main axis is perpendicular.

The basket holder can be rotated by the main drive at a nominal speed of at least 30 revolutions per minute and a maximum of 220 revolutions per minute. Particularly good results were achieved with a nominal speed of about 200 revolutions per minute. The main drive is preferably dimensioned in such a way that the desired rated speed can be reached within a maximum of 10 seconds and more preferably within about 5 seconds. During the centrifugal process, the centrifuge baskets or the mass parts that are taken up can be subjected to loads of more than 20 times the gravitational acceleration or the weight G. Preferably, the load factor is between 20 and 80. In particular, the load factor can be about 25 to 40 and more preferably about 32. The n-fold of the weight force G is referred to as the load factor n. During system operation, the rated speed can be maintained for a time interval of at least 10 seconds to 60 seconds. In particular, the rated speed can be maintained for about 30 seconds. The nominal speed is preferably at least 60 revolutions per minute and more preferably more than 100 revolutions per minute. In addition, the at least one motor of the auxiliary drive device can drive the centrifuge baskets to rotate about their basket axes. The basket speed can be up to 15 revolutions per minute. Overall, this ensures that excess treatment liquid is effectively thrown off the mass parts, so that by specifying the rotation duration, the nominal speed, the direction of rotation and the speed of rotation of the centrifuge baskets around the basket axes (in the same direction and/or in the opposite direction to the direction of rotation of the basket carrier the main axis), etc. the amount of coating liquid remaining on the mass parts and thus the layer thickness can be influenced. For example, the longer the rated rotation speed is maintained and the higher the rated rotation speed is, the more coating liquid is thrown off, with the result that the coating thickness on the mass parts is thinner. In order to obtain thicker layers, for example, the rotation time and the nominal speed can be reduced.

The support element, in relation to which the longitudinal shaft is rotatably mounted, can be a crossbeam of the support structure. The transom can have a bore through which the longitudinal shaft passes. The main drive of the main drive device can be attached to the support element. The support element can be rigidly integrated as a crossbeam of the support structure or can be pivoted about a horizontal axis on a stationary part of the support structure.

Preferred embodiments of the invention are illustrated in the drawings and described below. Herein shows:

FIG. 1 shows a system according to the invention for treating mass parts contained in two centrifuge baskets according to a first embodiment in a perspective side view obliquely from above;

FIG. 2 shows a perspective view of the system from FIG. 1 in a perspective sectional representation;

FIG. 3 shows an enlarged partial view of the system;

FIG. 4 shows an enlarged partial aspect of the plant from the perspective view shown in FIG. 2;

FIG. 5 shows a reduction gear of the system from FIG. 1 in a perspective view obliquely from above;

FIG. 6 shows the reduction gear in a perspective view obliquely from below; FIG. 7 shows a partial section through the reduction gear;

FIG. 8 shows an enlarged partial aspect of the plant from the perspective view shown in FIG. 4;

FIG. 9 shows a plan view from above of a basket carrier of the system from FIG. 1;

FIG. 10 shows an enlarged partial illustration of the basket carrier of the system from FIG. 1;

FIG. 11 shows an enlarged partial illustration of a connection arrangement of the system from FIG. 1;

FIG. 12 is a perspective view from below of the system of FIG. 1, the system being shown without the centrifuge baskets;

FIG. 13 shows a plant according to the invention for treating mass parts contained in two centrifuge baskets according to a second embodiment in a side view, with the plant being shown in an initial position;

FIG. 14 shows the system from FIG. 13 in a sectional view, the system being shown in a pivoted position in which the centrifuge baskets are immersed in a dip tank;

FIG. 15 shows a system according to the invention for treating mass parts contained in four centrifuge baskets according to a third embodiment in a schematically simplified view, in which a basket carrier is shown from below; and

FIG. 16 shows a system according to the invention for treating mass parts contained in four centrifuge baskets according to a fourth embodiment in a schematically simplified view, in which a basket carrier is shown from below. FIG. 1 shows a system for treating bulk parts contained in two centrifuge baskets 1 according to a first embodiment. Figures 2 to 12 show further details of this system. The system is used for coating pourable mass parts (not shown), such as screws, stamped parts or the like, with the mass parts to be coated being immersed in a coating liquid (not shown) and then thrown outside of the coating liquid.

It can be seen in FIG. 1 that the system has a support structure 2 in the form of a stationary frame. The support structure 2 is supported on a stationary floor 3 and encloses a working space 4. To clarify the orientation of the support structure 2, the three spatial directions X, Y and Z are shown in FIG. The spatial direction Z runs parallel to the vertical, or to the direction of gravity. The designations "below", "above", "below" and "above" are to be understood as position information in relation to the Z-direction. “Horizontal” means an extension parallel to a plane spanned by the two spatial directions X and Y.

The system also has a basket carrier 5 on which the two centrifuge baskets 1 are held in a reversibly detachable manner. The basket carrier 5 is held in the working space 4 hanging freely on a longitudinal shaft 6 of a main drive device 7 . The longitudinal shaft 6 is rotatably mounted about a main axis A relative to a support element 8 of the support structure 2 and can be driven in rotation about the main axis A by a main drive 9 of the main drive device 7 . The main drive 9 is attached to the support element 8 . The support element 8 can be a crossbeam that is rigidly integrated into the support structure 2 . The main drive 9 can be an electric motor that is connected to an electrical power supply 10 of the system. By means of the main drive 9, the basket carrier 5 can preferably be driven to rotate about the main axis A within five seconds to a desired nominal speed, with the nominal speed being able to be more than 30 revolutions and less than 220 revolutions per minute.

The basket carrier 5 has a base body 11 with a central bore 12, see in particular FIG. 10. In the central bore 12 is a lower or dem Basket carrier 5 facing the end of the longitudinal shaft 6 used, to clarify the structure of the basket carrier 5, the longitudinal shaft 6 is not shown in Figure 10. The longitudinal shaft 6 and the base body 11 can be connected to one another by means of a standardized shaft-hub connection, such as a positive connection with a groove 13 and a feather key (not shown). The base body 11 has an elongate base plate 14 and two side walls 15 spaced apart from one another. The side walls 15 protrude perpendicularly from the base plate 14 on an upper side 16 facing the support element 8 and can have a trapezoidal basic shape. The base plate 14 is oriented horizontally.

An auxiliary drive device 17 for rotating the centrifuge baskets 1 about a basket axis K radially spaced from the main axis A is arranged between the side walls 15 on the base body 11 . Due to their eccentric arrangement, the two basket axes K can also be referred to as planetary axes of rotation. The auxiliary drive device 17 has a motor 18 and a power transmission train 19 for each centrifuge basket 1 . The motors 18 are electric motors, in particular servomotors. The longitudinal shaft 6 is designed as a hollow shaft through which electrical lines 20 are routed in order to connect the motors 18 to an electrical power supply 10 of the system. Furthermore, control lines 21 , in particular bus lines for connecting the auxiliary drive device 17 to a control unit 22 of the system, can be routed through the longitudinal shaft 6 . The main drive device 7 can also be connected to the control unit 22 .

In order to reduce the centrifugal forces acting on the motors 18 to a minimum during rotation of the basket carrier 5 about the main axis A, the motors 18 are attached to the main body 11 as close as possible to the main axis A. Specifically, the motors 18 each have a rotor shaft 23 which can be driven in rotation about a rotor axis D aligned parallel to the main axis A. The respective rotor axis D is arranged away from the main axis A at a distance R1 of at most 300 millimeters and can have a distance R1 of between approximately 140 millimeters and 180 millimeters. To avoid imbalances, the motors 18 are arranged symmetrically with respect to the main axis A on the base body 11. The rotor axes D preferably lie on an imaginary first circle C1, which is arranged concentrically to the main axis A and has the radius R1, as shown in FIG. The basket axes K can on the other hand lie on an imaginary second circle C2, the radius R2 of which is greater than the radius R1. In particular, the radius R1 can be smaller than 0.5 times the radius R2.

The power transmission strands 19 each have a belt drive 24 . The respective belt drive 24 is described below. It goes without saying that the statements apply to both belt drives 24, which are identical in construction. The belt drive 24 has a toothed belt 25 and two toothed pulleys, namely a drive pulley 26 and a driven pulley 27 on. The drive disk 26 is fastened concentrically to the rotor axis D on the rotor shaft 23 of the associated motor 18 . The driven disk 27 is fastened concentrically to the basket axis K on an input shaft 28 designed as a hollow shaft. Furthermore, the belt drive 24 has a permanently adjustable tensioning device with a first tensioning roller 29 and a spring-loaded tensioning device with a second tensioning roller 30 . The transmission ratio (abbreviated to "i"), which is defined as the quotient of the speed of the transmission input (here: the drive pulley 26) and the speed of the transmission output (here: driven pulley 27), can be in a range of i = 1 for the belt drive 24 .5 to i = 10. Here the transmission ratio is in a range from i = 2 to i = 6. Because i > 1, the speed is reduced (“transmission to slowdown”) and the transmittable torque is increased. The respective belt drive expediently has a fixed transmission ratio.

Furthermore, the power transmission lines 19 each have a reduction gear 31, as a result of which the torque that can be transmitted is increased further. As a result, the centrifuge baskets 1 can be rotated about the basket axes K with a sufficiently high torque of, for example, 1000 to 2500 Newton meters. The reduction gears 31 can be eccentric gears known per se. An eccentricity on the rotating input shaft 28 can produce a cycloid movement, which entrains needles arranged circumferentially distributed around the basket axis K in a gear housing 68 of the respective reduction gear 31 . Such a reduction gear 31 is, for example, the TwinSpin reduction gear from the G series from Spinea®. Particularly good results in terms of the reduction ratio and the associated increase in torque and longevity have been achieved, for example, with the reduction gear model TS 335G from the Spinea ® G series. The respective reduction gear 31 is described below. It goes without saying that the statements apply to both reduction gears 31, which are identical in construction. The reduction gear 31 is shown in detail in FIGS.

The reduction gear 31 is inserted in a through hole 69 in the base plate 14 of the base body 11 and firmly connected to the base body 11, in particular screwed. The transmission housing 68 is designed in particular in the form of a flange and has a stepped outer wall. A first outer wall section 70 of the gear housing 68, which is inserted in the base plate 14, can have a smaller outer diameter than a second outer wall section 71 of the gear housing 68 projecting beyond the base body 11 on the basket side. The inner diameter of the through hole 69 corresponds at least essentially to the outer diameter of the first outer wall section 70 of the gear housing 68. The gear housing 68 of the reduction gear 31 projects on an underside 33 of the base body 11 facing away from the top 16. Here, the reduction gear 68 was inserted from below into the through hole 69 in the base plate 14 and, in particular, screwed to it from below.

The input shaft 28 is the transmission input side shaft of the reduction gear 31 . The input shaft 28 is mounted in the gear housing 68 so as to be rotatable about the basket axis K concentrically to the basket axis Kund. The reduction gear 31 has a hollow output element 32 on the gear output side. The output element 32 has a hollow-cylindrical output shaft 80 and an output flange 81 connected to the output shaft 80 in a torque-proof manner. The output flange 81 and the output shaft 80 are, here, screwed together by means of screws 82, only a subset of the screws being provided with the reference number for the sake of clarity. The output shaft 80 is inserted in the hollow input shaft 28 and can be mounted by means of a bearing 83, in particular a needle bearing, so that it can rotate about the axis K of the basket. The hollow output element 32 thus forms a passage 73 through the reduction gear 31 .

The transmission ratio (abbreviated with "i") of the reduction gear 31, which is the quotient of the speed of the gear input (here: the input shaft 28) and speed of the transmission output (here: the output element 32) is defined, can be in a range from i=50 to i=200 for the reduction gear 31. In particular, the reduction ratio can be between i=90 and i=120.

An outside diameter of the output element 32, in particular of the output flange 81, can be more than four times the outside diameter of the input shaft 28. FIG. 7 shows that this ratio is preferably about 5 to 1. Preferably, this ratio is less than 8 to 1 and more preferably less than 6 to 1.

A flange-like rotary platform 34 is fastened to the lower or basket-side end of the respective output element 32 , in particular to the output flange 81 . The gear housing 68 protrudes from the underside 33 of the base body 11 and the driven element 32 protrudes beyond the gear housing 68 by about 0.5 millimeters to 5 millimeters and, here, preferably by about 1 millimeter. The rotating platform 34 is fastened to the driven element 32 in a hanging manner and can be driven by the protruding driven element 32 to rotate about the basket axis K without collision. The rotary platform 34 can be screwed to the output element 32 with a large number of screws 75 distributed around the circumference, in which threaded bores 84 distributed around the circumference are incorporated for this purpose. In particular, the rotary platform 34 may be secured to the output member 32 with twenty to thirty of the screws 75 to keep the rotary platform 34 hanging freely from the output member 32 . The flange-like rotating platforms 34 can each have an opening 35 configured concentrically to the basket axis K.

It can be seen in particular in FIG. 8 that the rotating platform 34 is in several parts and has an annular first plate 76 which is fastened to the driven element 32 with the screws 75 . A second ring-shaped plate 77 , which is screwed to the first plate 76 by means of a large number of screws 78 , connects radially further to the outside. The second plate 77 is arranged on the first plate 76 from above, or from the side facing away from the basket. The respective centrifuge basket 1 can be detachably fastened to the rotary platform 34 . In order to withstand the forces occurring in the operation of the system in the axial and radial direction as well as the moments such as tilting moments, to withstand, the output element 32 is inserted in a housing opening 72 of the gear housing 68 and rotatably mounted relative to the gear housing 68 about the basket axis K. For example, roller bearings, in particular barrel bearings, can be provided, which can also be rotated alternately by 90 degrees in several rows or in the circumferential direction in order to be able to absorb the radial and axial forces. The outside diameter of the output member 32 can correspond to about 75 percent to 95 percent, and preferably about 85 percent, of an outside diameter of the transmission housing 68 in the second outer wall section 71 . A bearing, in particular a barrel bearing, is preferably arranged between the peripheral surface of the output element 32 and the inner wall of the transmission housing 68 . A sealing ring 79 can connect axially below the bearing. The rotary platforms 34 attached to the output elements 32 are thus drive-connected to the assigned motor 18 via one of the power transmission lines 19 and can be driven independently of one another by the respectively assigned motor 18 to rotate about the respective cage axis K due to the mechanical separation of the two power transmission lines 19.

For the reversibly detachable connection of the centrifuge baskets 1 to the basket carrier 5, a connection arrangement 36 is provided for each centrifuge basket 1. The connection arrangements 36 each have three connector units 37 here. The connector units 37 are evenly distributed around the cage axis K in the circumferential direction and, as can be seen in particular in FIG. 12, can be arranged at the same distance from the respective cage axis K. The connector units 37 each have a first connector in the form of a clamping module 38 and a second connector in the form of a connecting bolt 39 . The clamping modules 38 are attached to the rotating platforms 34 and the connecting bolts 39 are attached to the centrifuge baskets 1 .

It can be seen in particular in FIG. 11 that the centrifuge baskets 1 each have a radially protruding connecting flange 40 at their open end. The connecting flange 40 is aligned perpendicularly to the basket axis K, at least when the centrifuge basket 1 is held on the basket carrier 5 . The connecting bolts 39 are fastened to the connecting flange 40 of the respective centrifuge basket 1 and protrude axially. The connecting bolts 39 each have a bolt axis B39 which is aligned parallel to the main axis A. The connection flange 40 can, as under Other things that can be seen in FIG. 9 have an oval base area or, as shown in FIG. 11, basically also have a triangular base area. Other footprints are also possible, such as a circular, rectangular, square, or polygonal footprint.

The clamping modules 38 are arranged in a section 77 of the respective rotary platforms 34 which protrudes radially beyond the reduction gear 31 . The rotary platforms 34 can have a round or angular basic shape, for example. The clamping modules 38 each have a module base body 74 in which a bolt receptacle 41 is formed which is open downwards, ie toward the respective centrifuge basket 1 , into which the connecting bolts 39 can be inserted. The bolt receptacles 41 each define a central axis B41 which, like the bolt axes B39, is aligned parallel to the main axis A. The bolt receptacles 41 are designed in a quasi cup-shaped manner. In order to radially fix the connecting bolts 39 in the inserted state, the respective module base body 74 encloses the bolt receptacle 41 in the circumferential direction around the central axis B41, in particular completely. The clamping modules 38 also each have a locking mechanism 59 which clamps the inserted connecting bolt 39 in the clamping module 38 (connected state). The connecting bolts 39 can each have a circumferential groove 42 into which positive-locking elements, in particular locking bolts of the locking mechanisms 59, can engage in the connected state. The positive-locking elements are preferably acted upon by springs towards the central axis B41, so that the connecting bolts 39 inserted into the bolt receptacles 41 in the connected state are clamped by spring force. The clamping modules 38 are pneumatically actuated centering clamps, known per se, which can be acted upon with compressed air to relax the locking mechanisms 59 or to displace the form-fitting elements against the spring force and thus away from the central axes B41. In a released state, the locking mechanisms 59 release the connecting bolts 39 again, so that the connecting bolts 39 can be displaced axially relative to the clamping modules 38 . In the released state, the centrifuge baskets 1 can thus be decoupled from the basket carrier 5, as shown in FIG.

The clamping modules 38 are connected to pneumatic lines 44 via plug-in couplings 43, which connect the clamping modules 38 to a pneumatic supply network 45 integrate into the plant. Furthermore, the control lines 21 and, if necessary, the power lines 20 can be routed to the clamping modules 38 in order to be able to connect them to the control unit 22 and, if necessary, to the electrical power supply 10 . Coming from the rotary platforms 34, the lines 44, 20, 21 are guided through the hollow input shafts 28 or the passage 73 of the output element 32 of the reduction gear 31 into a secondary rotary passage 46. The secondary rotary passages 46 are each connected to one of the Turning platform 34 facing away from the end of the output element 32, in particular the output shaft 80 connected. The components inside the reduction gear 31 are mostly removed in FIGS. 2, 4 and 8 only to clarify the structure. It can be seen that a first body 47 of the respective secondary rotary feedthrough 46 is supported relative to the base body 11 of the basket carrier 5 . A second body 48 of the respective auxiliary rotary feedthrough 46 is connected to the output shaft 80 in a rotationally fixed manner. For this purpose, a plurality of threaded bores 85 distributed around the circumference are formed in the end face of the output shaft 80 in order to screw the second body 48 to the output shaft 80 . In a manner known per se, the secondary rotary feedthroughs 46 enable the sealed transition of the pneumatic lines 44 between the stationary first bodies 47 and the second bodies 48, which can be driven to rotate about the basket axes K.

The pneumatic lines 44 are routed on the upper side 16 of the base body 11 towards the main axis A and are connected to a Y-connector 49 there. The Y connector 49 is connected to a central pneumatic line 50, which is routed through the longitudinal shaft 6 designed as a hollow shaft. A central rotary feedthrough 51 is arranged on an upper end of the longitudinal shaft 6 facing away from the basket carrier 5 . The central rotary feedthrough 51 has a first body 52 which is supported in relation to the supporting structure 2 . A second body 53 of the central rotary feedthrough 51 is connected to the longitudinal shaft 6 in a rotationally fixed manner. The electrical lines 20 and the control lines 21 for the secondary drive device 17 and the pneumatic line 44 for the clamping modules 38 are routed through the central rotary bushing 51 . Contact points 54 for connecting the electrical lines 17 to the power supply 10 and for connecting the control lines 21 to the control unit 22 are arranged on the first body 52 of the central rotary feedthrough 51 . Continue- towards a pneumatic coupling 55 is arranged on the first body 52 of the central rotary leadthrough 51, via which the pneumatic line 50 can be connected to the pneumatic supply network 45.

In FIG. 12, the system is shown diagonally from below. It can be seen that a cover 56 is arranged between the clamping modules 38 arranged on the rotary platforms 34 for each rotary platform 34 . The covers 56 are used to close the centrifuge baskets 1 , which are open at the top, when they are held on the basket carrier 5 . The centrifuge baskets 1 have walls 57 that are perforated or provided with holes, which the coating liquid can penetrate. The walls 57 divide the respective centrifuge basket 1, here, into three spatially separate chambers 58 for accommodating the mass parts. The chambers 58 are distributed in the circumferential direction and are open at the top in order to be able to fill in the bulk parts. The centrifuge baskets 1 are rotationally symmetrical to the basket axis K. By dividing the centrifuge baskets 1 into the chambers 58, the restoring moments when the centrifuge baskets 1 rotate about the basket axes K are minimized. As a result, the centrifuge baskets 1 filled with the mass parts can be rotated more easily about the basket axes K, as a result of which the load on the motors 18 is reduced.

FIGS. 13 and 14 show a plant for treating mass parts contained in two centrifuge baskets 1 according to a second embodiment. This embodiment differs from the above-described first embodiment according to FIGS. 1 to 12 only in that the support element 8 is integrated in the support structure 2 so that it can pivot about a horizontal pivot axis S, so that reference is made to the above explanations with regard to the similarities. Overall, the same details are provided with the same reference symbols as in FIGS. 1 to 12. To clarify the orientation of the support structure 2, the three spatial directions X, Y and Z are shown in FIGS. The spatial direction Z runs parallel to the vertical, or to the direction of gravity. The designations "below", "above", "below" and "above" are to be understood as position information in relation to the Z-direction. “Horizontal” means an extension parallel to a plane spanned by the two spatial directions X and Y.

The support member 8 can be a U-shaped swing frame, the side of two horizontal side struts 60 of the support structure 2 is pivotally supported. Two hydraulic cylinders 61 can be provided for pivoting, which are supported on the side struts 60 and the support element 8 . In order to bridge the pivoting movements, the lines 20 , 21 , 51 can be routed via one or more energy supply chains 62 from the central rotary feedthrough 51 to a fixed frame 63 of the support structure 2 .

A paint carriage 64 with a dip tank 65 is positioned in the working space 4 and can be pushed into the working space 4 from the side and pushed out of it again. The coating liquid 66 is contained in the dip tank 65 . In order to be able to raise or lower the paint carriage 64 with the dip tank 65 , a lifting device 67 can be attached to the stationary part of the support structure 2 and is supported on the floor 3 . The plunge pool 65 can thus be displaced along a vertical axis that extends along the Z spatial direction. The lifting device 67 can also be used in the system according to the first embodiment, as shown in FIGS.

In the figure 13, the system is shown in an initial position in which the paint truck

64 is parked on the floor 3. The main axis A of the longitudinal shaft 6, on which the basket carrier 5 hangs, is oriented vertically. The basket carrier 5 and the centrifuge baskets 1 stand still. In FIG. 14 the immersion basin arranged on the paint carriage 64 is shown

65 has approached the basket carrier 5 from below. The centrifuge baskets 1 are immersed in the coating liquid 66 . The support element 5 is pivoted about the pivot axis S, so that the basket axes K enclose an angle of, here, about 30 degrees with the floor 3 . The motors 18 drive the rotating platforms 34 in rotation about the basket axes K in order to circulate the mass parts contained in the centrifuge baskets 1 in the coating liquid 66 .

FIGS. 15 and 16 show further possible geometries of the basket carrier 5, which, as shown in FIG. 15, can form a circular area or, as shown in FIG. 16, can have the shape of a cross or a plus sign. Reference List

1 centrifuge basket 28 input shaft

2 supporting structure 29 idler pulley

3 floor 30 idler pulley

4 working space 31 reduction gear

5 basket carrier 32 output element

6 propeller shaft 33 underside

7 main propulsion device 34 rotary platform

8 support element 35 opening

9 Main drive 36 connection arrangement

10 power supply 37 connector unit

11 basic body 38 clamping module

12 hole 39 connecting bolt

13 groove 40 connection flange

14 Base plate 41 Bolt mount

15 sidewall 42 groove

16 top 43 plug-in coupling

17 power take-off device 44 pneumatic line

18 engine 45 pneumatic supply network

19 power train 46 sub-rotary union

20 electric line 47 first body

21 control lines 48 second body

22 control unit 49 Y connector

23 rotor shaft 50 pneumatic line

24 belt drive 51 rotary union

25 toothed belt 52 first body

26 drive pulley 53 second body

27 driven pulley 54 contact point Clutch 80 output shaft

Cover 81 outlet flange

wall 82 screw

Chamber 83 camp

Locking mechanism 84 threaded hole

Side brace 85 threaded hole

hydraulic cylinder

cable drag chain

framework

paint truck

plunge pool

coating liquid

lifting device

Transmission housing A main axle

Through hole B bolt axis, central axis

Outer wall section C imaginary circle

Outer wall section D Rotor axis

Housing opening K basket axis

Opening R radius

Module base S swivel axis

Screw X spatial direction

Plate Z direction in space

plate

screw

sealing ring

Claims

Plant for treating mass-produced parts with a power take-off device claims

1 . Plant for treating mass-produced parts, the plant comprising: a support structure (2) with a support element (8), a basket carrier (5) for at least two centrifuge baskets (1), a main drive device (7) fixed to the support structure (2) and having a Main drive (9) and a longitudinal shaft (6), wherein the longitudinal shaft (6) is mounted rotatably about a main axis (A) relative to the support element (8) and can be driven in rotation about the main axis (A) by the main drive (9), the Basket carrier (5) suspended from the longitudinal shaft (6) and connected to the longitudinal shaft (6) in a rotationally fixed manner, and an auxiliary drive device (17) with at least one motor (18) and one power transmission line (19) for each centrifuge basket (1) for rotating the centrifuge basket (1) about a basket axis (K) which is radially spaced from the main axis (A), the at least one motor (18) of the auxiliary drive device (18) being arranged on the basket carrier (5), characterized in that the respective power transmission line (19 ) a reduction gear (31) with a gear housing (68) which is fastened to the basket carrier (5), an input shaft (28) which can be driven in rotation by the at least one motor (18) and an output element ( which is coaxial with the basket axis (K) 32), wherein a transmission ratio between an input speed of the input shaft (28) and an output speed of the output element (32) is greater than one. System according to claim 1, characterized in that an outer diameter of the output element (32) of the respective reduction gear (31) corresponds to 0.5 times to 1.0 times an outer diameter of the gear housing (68). System according to claim 1 or 2, characterized in that the transmission ratio i of the respective reduction gear (31) is in a range from i = 50 to i = 200. System according to one of Claims 1 to 3, characterized in that the at least one motor (18) has a maximum rated output of 5000 watts. System according to one of Claims 1 to 4, characterized in that the power transmission lines (1) each have a belt drive (24) which can be driven in rotation by the at least one motor (18) and which is drive-connected to the input shaft (28) of the respective reduction gear (31). is. System according to one of Claims 1 to 5, characterized in that the at least one motor (18) has a rotor shaft (23) which can be driven in rotation about a rotor axis (D), the rotor axis (D) being on an imaginary first circle (C1) and the basket axes (K) are arranged on an imaginary second circle (C2), with the first circle (C1) and the second circle (C2) being arranged concentrically to the main axis (A) and a first radius (R1) of the first circle (C1 ) is smaller than a second radius (R2) of the second circle (C2). System according to Claim 6, characterized in that the first radius (R1) is less than 0.5 times the second radius (R2) and/or that the first radius (R1) is less than 300 millimeters. System according to one of Claims 1 to 7, characterized in that the longitudinal shaft (6) is designed as a hollow shaft, through which a supply line (20) for connecting the at least one motor (18) to a supply system (10) of the system from the supporting structure (2) are led to the basket carrier (5). System according to Claim 8, characterized in that a central rotary feedthrough (51) for the supply line (20) is arranged on one end of the longitudinal shaft (6) remote from the basket carrier (5), the central rotary feedthrough (51) having a bearing structure ( 2) supported first body (52) and a second body (53) non-rotatably connected to the longitudinal shaft (6). System according to one of Claims 1 to 9, characterized in that the output element (32) of the respective reduction gear (31) has an output flange (81) and a hollow-cylindrical output shaft (80) connected to the output flange (81), the output shaft (80 ) is used in the input shaft (28) and is rotatably mounted relative to this about the respective cage axis (K). System according to one of Claims 1 to 10, characterized in that a flange-like rotary platform (34) for the detachable connection of the respective centrifuge basket (1) is held hanging on the output element (32), in particular the output flange (81) of the respective reduction gear (31) and is non-rotatably connected to the output element (32). System according to Claim 11, characterized in that each centrifuge basket (1) has a connection arrangement for the reversibly detachable connection of the respective centrifuge basket (1) to the basket support (5), the first connector (38) of the connection arrangements (36) being on the rotating platforms (34) and with the first connectors (38) connectable second connector (39) of the connection arrangements (36) are arranged on the centrifuge baskets (1). System according to Claim 12, characterized in that the first connectors (38) are pneumatically actuable clamping modules, pneumatic and/or electrical lines (44) for actuating the first connectors (38) from the supporting structure (2) through the longitudinal shaft designed as a hollow shaft (6) are guided to the basket carrier (5). System according to Claim 13, characterized in that the pneumatic and/or electrical lines (44) for actuating the first connector (38) are guided through the input shafts (28) of the reduction gear (31), which are designed as hollow shafts. System according to Claim 13 or 14, characterized in that on the basket carrier (5) for each rotary platform (34) there is a secondary rotary bushing (46) for the pneumatic and/or electrical lines (44) for actuating the first connectors (38). , wherein the secondary rotary leadthroughs (46) each have a first body (47) supported against a base body (11) of the basket carrier (5) and a second body (48) non-rotatably connected to the rotary platform (34).