Classifications

• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
  • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
  • B05B3/00—Spraying or sprinkling apparatus with moving outlet elements or moving deflecting elements
  • B05B3/02—Spraying or sprinkling apparatus with moving outlet elements or moving deflecting elements with rotating elements
  • B05B3/10—Spraying or sprinkling apparatus with moving outlet elements or moving deflecting elements with rotating elements discharging over substantially the whole periphery of the rotating member
  • B05B3/1035—Driving means; Parts thereof, e.g. turbine, shaft, bearings
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
  • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
  • B05B5/00—Electrostatic spraying apparatus; Spraying apparatus with means for charging the spray electrically; Apparatus for spraying liquids or other fluent materials by other electric means
  • B05B5/025—Discharge apparatus, e.g. electrostatic spray guns
  • B05B5/04—Discharge apparatus, e.g. electrostatic spray guns characterised by having rotary outlet or deflecting elements, i.e. spraying being also effected by centrifugal forces
  • B05B5/0415—Driving means; Parts thereof, e.g. turbine, shaft, bearings
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
  • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
  • B05B3/00—Spraying or sprinkling apparatus with moving outlet elements or moving deflecting elements
  • B05B3/001—Spraying or sprinkling apparatus with moving outlet elements or moving deflecting elements incorporating means for heating or cooling, e.g. the material to be sprayed
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
  • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
  • B05B3/00—Spraying or sprinkling apparatus with moving outlet elements or moving deflecting elements
  • B05B3/003—Spraying or sprinkling apparatus with moving outlet elements or moving deflecting elements with braking means, e.g. friction rings designed to provide a substantially constant revolution speed

Definitions

• the invention relates to a turbine drive for a rotary atomizer and a corresponding operating method.
• WO 2016/062365 A1 EP 1 384 516 A2 and DE 44 25 229 A1 , WO 2006/024861 A1 , WO 2016/116275 A1 , WO 2016/062365 A1 , and DE 101 15 469 A1 .
• the invention is therefore based on the objective of creating a correspondingly improved turbine drive for a rotary atomizer. Furthermore, the invention also aims to... The basis for this is to specify a suitable operating procedure for such a turbine drive.
• the invention is based on the technical-physical insight that the turbine in a rotary atomizer is often not operated at an optimal load point during operation, the load point being determined by the rotational speed and the torque.
• the invention is based on the fact that turbine nozzles can only be optimized for a specific load point with regard to shape and nozzle cross-section. Therefore, the various load points occurring during the operation of a rotary atomizer mean that the turbine is not always operated at its optimal load point. However, operating the turbine at a suboptimal load point leads to a reduction in turbine efficiency. Thus, optimizing the turbine for exterior painting results in relatively poor efficiency for interior painting. Conversely, optimizing the turbine for interior painting results in relatively poor efficiency for exterior painting.
• the invention therefore provides that the turbine has several drive nozzles, each supplied with its respective drive gas (e.g., compressed air) from separate drive gas feeds, so that the different drive nozzles can be activated or deactivated independently of one another. Depending on the respective load point, one or the other drive nozzles can then be activated. This makes it possible to operate the turbine in an optimal operating state even under changing load points, thereby increasing the efficiency of the The turbine is increased at changing load points.
• respective drive gas e.g., compressed air
• certain nozzles may be optimized for exterior painting, while others are optimized for interior painting.
• the nozzles optimized for exterior applications are selected.
• the nozzles optimized for interior applications are specifically chosen.
• the turbine drive according to the invention is designed for a rotary atomizer, as is known per se from the prior art and is found, for example, in EP 1388 372 A1 is described.
• the turbine drive according to the invention in accordance with the known turbine drive, features a rotatable turbine wheel with several turbine blades.
• the turbine is designed as a radial turbine; however, a design as an axial turbine is also possible in principle.
• the turbine according to the invention in accordance with the known turbine described above, has at least two drive nozzles to supply the turbine blades of the rotatable turbine wheel with a drive gas (e.g. compressed air) in order to drive the turbine wheel.
• a drive gas e.g. compressed air
• the invention provides that the various drive nozzles are supplied with drive gas from separate drive gas supplies, with the drive gas supplies being separate from one another so that the drive nozzles can be supplied with drive gas independently. This makes it possible to select and supply the most suitable drive nozzle with drive gas depending on the respective load point of the turbine drive, while the other drive nozzles are deactivated and not supplied with drive gas.
• the invention thus enables a targeted selection and activation or deactivation of the individual drive air nozzles depending on the load point in order to optimize the efficiency of the turbine accordingly.
• three different drive nozzles and Three drive gas supplies are provided, which are separate from each other and can be operated independently.
• the invention is not limited to a specific number of drive nozzles and separate drive gas supplies.
• more than three drive nozzles and, accordingly, more than three drive gas supplies can be provided.
• multiple groups of drive nozzles can be provided, with each group's drive nozzles being supplied with drive gas (e.g., compressed air) via a common drive gas supply.
• drive gas e.g., compressed air
• a first group of drive nozzles could be optimized for exterior painting, while a second group is optimized for interior painting.
• the drive nozzles of one of the two groups are then selected and supplied with drive gas, while the drive nozzles of the other group remain inactive.
• the various drive nozzles are preferably different, for example, in terms of their nozzle shape and/or their nozzle cross-section. This is advantageous so that, depending on the respective load point, the most suitable drive nozzle can be selected for the flow towards the turbine blades of the turbine wheel. It should also be mentioned that, as a rule, not just a single drive nozzle is selected. For example, several drive nozzles can be selected simultaneously, depending on the respective load point.
• the individual drive nozzles may preferably have a convergent-divergent nozzle cross-section. This means that the nozzle cross-section initially narrows convergently in the flow direction and then widens again divergently, as is the case, for example, with a Laval nozzle.
• the turbine wheel can also be braked by releasing a braking gas (e.g., compressed air) from a braking nozzle onto the turbine blades of the turbine wheel, with the braking nozzle being oriented opposite to the at least one drive nozzle.
• a braking gas e.g., compressed air
• the turbine drive according to the invention also preferably provides such a braking nozzle, which is preferably supplied with the respective braking gas (e.g., compressed air) from a braking gas supply via a braking gas control valve.
• the drive nozzles are supplied individually or in groups with the respective drive gas (e.g., compressed air) via separate drive gas supplies.
• Each drive gas supply preferably contains a drive gas control valve, which can, for example, be designed as a proportional valve and is preferably pneumatically actuated.
• pneumatic actuation of the drive gas control valves electrical or other actuation is also possible.
• the invention provides for the possibility of arranging a bistable spring element in at least one of the drive gas supply lines, which either opens or closes the respective drive gas supply line depending on its state.
• the bistable spring element is thus a bistable valve, wherein the bistable spring element is preferably connected to the brake gas supply line and changes its state upon a pressure impulse in the brake gas supply line.
• bistable spring element can also be implemented with multiple drive nozzles, meaning that a bistable spring element can be arranged in each of the individual drive gas inlets.
• this results in inefficient flow through the respective drive gas inlet, as there is only a single brake gas inlet.
• the turbine drive according to the invention can have a gas heater to heat the drive gas and/or the braking gas (e.g. compressed air) upstream of the drive nozzles or upstream of the braking nozzle, wherein the gas heater is preferably arranged outside the rotary atomizer.
• the gas heater e.g. compressed air
• the gas heater only heats the drive gas in one of the drive gas feeds, while the drive gas in the other drive gas feed(s) is not heated by the gas heater.
• the gas heater heats the drive gas in several and preferably in all drive gas feeds.
• the gas heater can, for example, be located upstream of the at least one drive gas control valve. Alternatively, it is also possible for the gas heater to be located downstream of the at least one drive gas control valve.
• the turbine drive according to the invention preferably also includes a turbine control unit which receives a load point on the input side, wherein the load point determines the rotational speed and/or torque of the turbine drive. On the output side, the turbine control unit then controls the drive gas control valves depending on the load point. In this process, the turbine control unit specifically selects the drive nozzles that promise optimal turbine efficiency at the respective load point.
• the turbine control system can open a different number of the drive gas control valves and close the remaining ones. Therefore, depending on the load point, the turbine control system can not only select the most suitable drive nozzle, but also vary the number of selected drive nozzles to increase turbine efficiency.
• the turbine drive according to the invention can have several drive gas shut-off valves in order to release or block the drive gas flows separately and independently of one another.
• a common drive gas proportional valve is preferably provided, which serves to adjust the sum of the individual drive gas flows, wherein the drive gas proportional valve is then arranged upstream of the drive gas shut-off valves.
• the invention claims, firstly, protection for the turbine drive described above, wherein the protection extends to the individual turbine, the rotary atomizer with such a turbine, and the turbine drive as a whole, which may also include the turbine control, the air heater, and other components.
• turbine drive used within the scope of the invention can therefore refer to the individual turbine, the rotary atomizer with such a turbine, or the complete turbine drive.
• the invention also claims protection for a corresponding operating method for such a turbine drive, wherein the individual steps of the operating method according to the invention are already evident from the foregoing description, so that a separate description can be dispensed with and reference is made to the foregoing description.
• the turbine drive powers a rotary atomizer 1, which is used for painting vehicle body components in a paint shop.
• the rotary atomizer 1 contains a turbine 2, which is largely of conventional design, as is the case, for example, in EP 1 388 372 A1 It is described, so reference is made to this publication as a supplement.
• turbine 2 features a rotatably mounted turbine wheel with numerous turbine blades distributed around its circumference.
• the turbine blades of the turbine wheel Compressed air can be supplied from two drive nozzles 3, 4 to drive the turbine wheel and thus the rotary atomizer 1.
• the two drive nozzles 3, 4 are supplied with compressed air from a compressed air supply 8, which can be referred to as a compressed air reservoir, compressed air compressor or pressure vessel, via separate drive gas supplies 5, 6 and an air heater 7.
• a compressed air supply 8 which can be referred to as a compressed air reservoir, compressed air compressor or pressure vessel, via separate drive gas supplies 5, 6 and an air heater 7.
• Each of the two drive gas inlets 5, 6 is equipped with a drive gas control valve 9, 10, which can independently control the drive gas flow to the individual drive nozzles 3, 4.
• the drive gas control valves 9, 10 are designed as proportional valves, which can be actuated, for example, pneumatically or electrically.
• the two drive gas control valves 9, 10 can then be controlled independently of each other in order to control the two drive nozzles 3, 4 accordingly.
• the control is carried out in such a way that optimal efficiency of the turbine 2 is achieved depending on the respective load point.
• turbine 2 has a braking nozzle 11, which makes it possible to slow down the turbine wheel by blowing compressed air onto the turbine blades.
• the braking nozzle 11 is therefore oriented opposite to the two drive nozzles 3 and 4.
• the brake nozzle 11 is supplied with compressed air via a brake gas supply 12 and a brake gas control valve 13.
• a special feature of this embodiment is that the two drive gas control valves 9, 10 are arranged upstream of the air heater 7, whereas in the embodiment according to Figure 1 are located downstream behind air heater 7.
• Another special feature of this embodiment is that the air heater 7 only heats the compressed air in the drive gas supply 5, whereas the other drive gas supply 6 is routed around the air heater 7.
• a special feature of this embodiment is that the air heater 7 enables separate and independent heating of the compressed air in the two drive gas supplies 5, 6.
• the compressed air in drive gas supply 5 can be heated more than the compressed air in the other drive gas supply 6.
• FIGS. 4A-4C show different views of a turbine 14 according to the invention, as it is in a similar form from EP 1 388 372 A1 is known, so this publication is also referenced.
• the turbine 14 has several housing parts 15-18 which, when assembled, accommodate a turbine wheel 19 with a turbine shaft 20 and numerous turbine blades 21, the turbine blades 21 being arranged distributed over the circumference of the turbine wheel 19.
• the housing part 16 contains three separate and independent drive gas supplies 25-27 to supply the three drive nozzles 22-24 independently with compressed air. to be able to supply. This enables the targeted selection of one or more of the drive nozzles 22-24 depending on the respective load point of the turbine 14, in order to achieve the greatest possible efficiency of the turbine 14.
• a brake nozzle 28 is formed in the housing part 16 of the turbine 14, which is supplied with compressed air from a brake gas supply 29.
• the brake nozzle 28 on the one hand and the drive nozzles 22-24 on the other hand are oriented in opposite directions according to their function (drive or brake).
• Figure 5 shows a schematic representation of a turbine drive according to the invention with three proportional valves 30-32 for controlling three drive nozzles, which are not shown here for the sake of simplicity.
• a brake valve 33 is shown to supply a brake nozzle with compressed air, although the brake nozzle is not shown here for the sake of simplicity.
• the proportional valves 30-32 and the brake valve 33 are controlled by a turbine control 34 depending on the respective load point in such a way that the turbine has the greatest possible efficiency.
• FIG. 6 shows a flowchart to explain the operating method according to the invention.
• a first step S1 the respective load point of the turbine is determined, which is defined by torque and rotational speed.
• step S2 the optimal combination of drive nozzles and drive air volume for the load point is then determined.
• step S3 the proportional valves for the individual drive nozzles are then controlled according to the optimal combination.
• Figure 7 shows a schematic representation of a turbine drive according to the invention with three drive nozzles 35-37, which are supplied with compressed air via three separate drive gas feeds 38-40.
• Each of the individual drive gas inlets 38-40 is equipped with a drive gas control valve 41-43, so that the drive nozzles 35-37 can be controlled independently of one another.
• the gas heater can be located upstream or downstream in separate chambers.
• the drive gas supplies 38-40 are combined on the inlet side via a proportional valve 44 and are supplied with compressed air from a common compressed air supply 45.
• Figure 8 Figure 1 shows a schematic representation of a turbine drive according to the invention, which largely corresponds to the embodiments described above, so that reference is made to the preceding description to avoid repetition, with the same reference numerals being used for corresponding details.
• a special feature of this embodiment is that the drive gas control valves 41-43 are proportional valves that are pneumatically controlled.
• FIG. 9 Another embodiment of a turbine drive according to the invention, which also largely corresponds to the embodiments described above, so that reference is made to the preceding description to avoid repetition, with the same reference numerals being used for corresponding details.
• a special feature of this embodiment is that a bistable spring element 46 is arranged in one of the drive gas supply lines 6, which is connected to the brake gas supply line 12 and switches between two stable states when a pressure impulse is applied in the brake gas supply line 12, namely between a first state in which the bistable spring element 46 blocks the drive gas supply line 6 and a second state in which the bistable spring element 46 releases the drive gas supply line 6.

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• Control Of Turbines (AREA)
• Nozzles (AREA)
• Electrostatic Spraying Apparatus (AREA)

Applications Claiming Priority (2)

Publications (2)

Family

ID=85477816

Family Applications (1)

Country Status (10)

Citations (1)

Family Cites Families (6)

• 2022
  • 2022-03-15 DE DE102022105999.5A patent/DE102022105999A1/de active Pending
• 2023
  • 2023-03-01 PL PL23709167.3T patent/PL4444475T3/pl unknown
  • 2023-03-01 US US18/843,718 patent/US20250178005A1/en active Pending
  • 2023-03-01 EP EP23709167.3A patent/EP4444475B1/de active Active
  • 2023-03-01 WO PCT/EP2023/055198 patent/WO2023174697A1/de not_active Ceased
  • 2023-03-01 KR KR1020247030642A patent/KR20240160117A/ko active Pending
  • 2023-03-01 ES ES23709167T patent/ES3055370T3/es active Active
  • 2023-03-01 MX MX2024010582A patent/MX2024010582A/es unknown
  • 2023-03-01 CN CN202380027557.1A patent/CN118891108A/zh active Pending
  • 2023-03-01 JP JP2024552014A patent/JP2025509153A/ja active Pending

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