WO1998037337A1 - Antriebseinheit für förderanlagen, insbesondere bandantriebsanlage - Google Patents
Antriebseinheit für förderanlagen, insbesondere bandantriebsanlage Download PDFInfo
- Publication number
- WO1998037337A1 WO1998037337A1 PCT/EP1998/000776 EP9800776W WO9837337A1 WO 1998037337 A1 WO1998037337 A1 WO 1998037337A1 EP 9800776 W EP9800776 W EP 9800776W WO 9837337 A1 WO9837337 A1 WO 9837337A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- circuit
- drive unit
- unit according
- coupled
- bypass circuit
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D33/00—Rotary fluid couplings or clutches of the hydrokinetic type
- F16D33/06—Rotary fluid couplings or clutches of the hydrokinetic type controlled by changing the amount of liquid in the working circuit
- F16D33/16—Rotary fluid couplings or clutches of the hydrokinetic type controlled by changing the amount of liquid in the working circuit by means arranged externally of the coupling or clutch
Definitions
- the invention relates to a drive unit for a conveyor system with a drive machine, a hydrodynamic coupling and a
- Operation of the drive unit can increase the belt life.
- these clutches and the operating medium circuit are designed in such a way that operating medium is constantly removed from the working circuit of the coupling and thus the heat generated during the power transmission.
- two systems are used:
- Fresh water pipe fed When using a double clutch, ie In a coupling with two circuits, the water control includes two water circuits. To start up, these - also known as working circuits - are filled with a large volume flow, while in continuous operation the system switches to a reduced volume flow. This serves to dissipate the heat generated during power transmission.
- a second known possibility is to convey the operating medium in a closed system with integrated cooling devices.
- the couplings are fed from a tank via connecting lines in the form of hoses.
- the level of the tank is located below the couplings.
- Coupling especially the work area, can flow back into the tank due to gravity.
- a pump is required for operation, which pumps the operating fluid in the tank into the working circuit of the coupling. Due to the power transmission through the equipment, it heats up. It is therefore on the outside
- Scope of the coupling spray nozzles is provided, via which a gradual escape of the equipment takes place.
- the removed, heated equipment collects in the equipment collection or coupling housing and from there returns to the tank due to gravity.
- Such a closed system is characterized in particular by a water-saving mode of operation, but requires an increased number of components and elements and an increased space requirement, in particular due to the need to provide supply lines between the tank and coupling and the necessary to implement the return
- a generic drive unit for a conveyor system with a drive machine and a hydrodynamic coupling, comprising a pump and a turbine wheel, which together form a work space that can be filled with operating fluid and to which an operating fluid supply system is assigned, is known from the publication DE 195 12 367 A1.
- the equipment supply system comprises a closed circuit.
- two further circuits in the form of a filling and emptying circuit are provided.
- the individual circuits can be switched on or off separately via valve devices.
- the disadvantage of such a design is essentially a complicated and long piping due to the long conduits.
- Valves of this kind which are constantly clocked, have a considerably shorter service life and the clocking itself leads to undesirable fluctuations in filling or speed in the drive system.
- the system is characterized by a considerably higher control engineering effort.
- the invention is therefore based on the object of integrating a hydrodynamic coupling in such a way into a drive system for conveyor systems, in particular belt drive systems, and of designing its supply of resources during the individual operating phases in such a way that the disadvantages of the known solutions are avoided and the effort for the control system can be minimized .
- Multi-motor drives make the entire filling system smaller while increasing the thermal capacity, the adjustment speed of the clutch is increased and the function of creep speed is improved.
- the entire unit should be able to work with as little external energy as possible.
- the equipment supply system comprises a closed circuit.
- bypass Circuit contains a bypass circuit.
- the bypass circuit there is an operating medium tank, which is located above the coupling and is therefore designed as a raised tank. A special pump for filling the coupling is therefore not necessary.
- Valves are also provided in the bypass circuit. The valves are controlled accordingly to fill the working area of the coupling.
- Bypass is understood to mean a line system arrangement which enables a bypass, here a bypass of the hydrodynamic coupling with at least partial utilization of the line systems of the closed circuit. This offers the advantage of simplified cable routing and piping.
- This design of the circuit with bypass circuit means that the clutch can be filled quickly when the drive machine starts up.
- the clutch can be designed, for example, as described in DE 42 24 728 A1.
- Fig. 1 illustrates schematically an embodiment of an equipment supply system of a hydrodynamic clutch according to the invention
- Fig. 2 shows a constructive embodiment of the hydrodynamic coupling in axial section
- Fig. 3 shows a plan view in the axial direction.
- FIG. 1 schematically illustrates an equipment supply system of a turbo coupling designed according to the invention, comprising two circuits, in particular for use in mining conveyor systems. Water is preferably used as the operating fluid.
- a circuit 1 can be seen in FIG. 1.
- This contains a hydrodynamic coupling 2, comprising a pump wheel and a turbine wheel, which together form a working space.
- the work area can be filled with operating resources.
- the clutch 2 is between a prime mover and one to be driven
- the circuit 1 further comprises a pump 3 for emptying the clutch 2.
- a temperature measuring device 4 follows. Furthermore, a cooler 5 is provided.
- a non-return valve 6 is located in a bypass line.
- a pressure measuring device 7, another non-return valve 8, an orifice 9 and a Venturi nozzle 10 follow.
- a bypass circuit 11 is connected to the circuit 1. This contains a 2/2-way valve 12, a tank 13 with a maximum level 13.1, a minimum level 13.2 and an overflow 13.3.
- a level switch 14 is assigned to the tank. Another 2/2-way valve 14 follows.
- the tank 13 is located above the coupling 2. Thus, no pump is required to fill the working space of the coupling 2.
- the bypass circuit 11 is coupled to the circuit 1 via the Venturi nozzle 10.
- Circuit 1 with bypass circuit 11 is a closed system. However, at some point you have to use equipment, e.g. with water. For this purpose, a connection 15 is provided. Between
- Connection 15 and bypass circuit 11 is connected to a 2/2-way valve 16, which can be bypassed by a bypass circuit with ball valve 17, and also an orifice 18.
- FIG. 2 illustrates one possibility of constructing the hydrodynamic clutch 2.
- This is designed, for example, as a double clutch, which has two toroidal working circuits 20 and 21, which are each formed by a primary wheel 22 or 23 and a secondary wheel 24 or 25.
- the two primary wheels are driven by a drive shaft 26.
- the two Secondary wheels are non-rotatably connected to an output shaft 27.
- the two primary wheels 22 and 23 are rotatably connected to one another by a cylinder section 28.
- the cylinder section 28 extends beyond the working space.
- This has a cover 30 which acts as a centrifugal disc and which extends symmetrically in the axial direction with respect to the two working spaces 20 and 21.
- the cylinder section 28 is also extended beyond the working space so that it forms a scooping space 29.
- the scooping chamber 29 itself rotates with the cylinder section 28.
- volume-adjustable bores or metering valves 31 through which the working fluid enters the scooping chamber 29.
- a scoop pipe not shown here, is provided, by means of which the leaked operating medium is conveyed into a return system.
- pre-chambers 32 and 33 are provided, shown in detail in FIG. 3. These each have an inlet opening 34 or 35.
- the prechambers are equipped with a peeling edge 36 and 37, the two peeling edges 36 and 37 each being designed and arranged such that the leakage liquid entrained by the centrifugal disc 30 is peeled off on its way up and into the respective prechamber 32 or 33 is initiated. Due to the double arrangement of the two antechambers 32 and 33 and the described design and arrangement of the peeling edges 36 and 37, operation in both directions of rotation is possible. In any case, however, the leakage liquid is peeled off from the centrifugal disc 30. Furthermore, a line 38 and 39 are provided, which the concerned
- the clutch 2 has a housing 40 which comprises a peripheral wall 41 which is essentially concentric with the clutch axis K and two substantially disk-shaped end walls 42 and 43.
- Antechambers 32 and 33 can be used, for example Circumferential wall 41 of the 40 housing are formed. However, other options are also conceivable.
- the antechambers are expediently arranged at the level of the axial middle plane and extend in the circumferential direction by a certain distance beyond this middle plane. The working fluid, which is due to leakage or when turning off the
- Coupling accumulated in the housing can be conveyed into the antechambers using the centrifugal disc. The losses due to acceleration and disc friction are minimal. The working fluid then flows from the antechambers into the rotating scooping chamber.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US09/171,665 US6220024B1 (en) | 1997-02-22 | 1998-02-12 | Drive unit for conveyors, in particular for a capstan system |
PL329375A PL192535B1 (pl) | 1997-02-22 | 1998-02-12 | Jednostka napędowa dla przenośnika, zwłaszcza dla przenośnika taśmowego |
AU63978/98A AU727786B2 (en) | 1997-02-22 | 1998-02-12 | A drive unit for conveyors, in particular for a capstan system |
GB9822133A GB2328494B (en) | 1997-02-22 | 1998-02-12 | A drive unit for conveyors, in particular a belt drive unit |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19707172A DE19707172C1 (de) | 1997-02-22 | 1997-02-22 | Antriebseinheit für Förderanlagen, insbesondere Bandantriebsanlage |
DE19707172.4 | 1997-02-22 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1998037337A1 true WO1998037337A1 (de) | 1998-08-27 |
Family
ID=7821209
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP1998/000776 WO1998037337A1 (de) | 1997-02-22 | 1998-02-12 | Antriebseinheit für förderanlagen, insbesondere bandantriebsanlage |
Country Status (7)
Country | Link |
---|---|
US (1) | US6220024B1 (de) |
AU (1) | AU727786B2 (de) |
DE (1) | DE19707172C1 (de) |
GB (1) | GB2328494B (de) |
PL (1) | PL192535B1 (de) |
WO (1) | WO1998037337A1 (de) |
ZA (1) | ZA981271B (de) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10122258B4 (de) * | 2001-05-07 | 2005-09-29 | Peter Huber | Kupplungseinheit |
DE10228026A1 (de) * | 2002-06-24 | 2004-01-22 | Bleichert Förderanlagen GmbH | Transporteinrichtung mit Hysteresekupplung |
DE10327133B4 (de) * | 2003-06-13 | 2006-01-12 | Voith Turbo Gmbh & Co. Kg | Hydrodynamische Kupplung und Antriebseinheit mit einer hydrodynamischen Kupplung |
DE102006031814A1 (de) * | 2006-07-07 | 2008-01-10 | Voith Turbo Gmbh & Co. Kg | Hydrodynamische Maschine |
DE102010022848A1 (de) | 2010-06-07 | 2011-12-08 | Voith Patent Gmbh | Hydrodynamische Kupplung |
DE102020202033A1 (de) | 2020-02-18 | 2021-08-19 | Bhs Corrugated Maschinen- Und Anlagenbau Gmbh | Betriebsmittel-Zuführanordnung |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE615344C (de) * | 1932-11-29 | 1935-07-04 | J M Voith Fa | Vorrichtung zum Betrieb hydraulischer Getriebe, die durch Fuellen eingerueckt und durch Entleeren ausgerueckt werden |
DE668327C (de) * | 1938-11-30 | J M Voith Maschinenfabrik | Turbogetriebe, insbesondere zum Antrieb von Kraftfahrzeugen | |
DE4224728A1 (de) | 1992-07-27 | 1994-02-10 | Voith Turbo Kg | Hydrodynamische Kupplung |
DE19512367A1 (de) | 1995-04-01 | 1996-10-02 | Voith Turbo Kg | Antriebseinheit für Förderanlagen, insbesondere Bandantriebsanlage |
Family Cites Families (20)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1859607A (en) * | 1928-10-17 | 1932-05-24 | Sinclair Harold | Hydraulic transmission gear and brake |
US2388112A (en) * | 1944-03-22 | 1945-10-30 | Twin Disc Clutch Co | Method and apparatus for cooling hydraulic coupling brakes |
US2634830A (en) * | 1946-07-26 | 1953-04-14 | Clayton Manufacturing Co | Apparatus and method for controlling dynamometers, etc. |
US2827989A (en) * | 1953-07-03 | 1958-03-25 | Gen Motors Corp | Hydrodynamic drive and brake |
US3051273A (en) * | 1959-07-15 | 1962-08-28 | Fiat Spa | Hydraulic brake |
DE2018652A1 (de) * | 1970-04-18 | 1971-12-02 | Daimler-Benz AG, 7000 Stuttgart-Untertürkheim | Hydrodynamische Bremse (Retarder) für Fahrzeuge, insbesondere Kraftfahrzeuge |
DE2203319A1 (de) * | 1972-01-25 | 1973-08-02 | Daimler Benz Ag | Dauerbremse fuer fahrzeuge, insbesondere fuer kraftfahrzeuge, vornehmlich schwere nutzfahrzeuge |
DE2260141A1 (de) * | 1972-12-08 | 1974-06-20 | Daimler Benz Ag | Hydrodynamischer retarder fuer fahrzeuge, insbesondere fuer kraftfahrzeuge |
US4051675A (en) * | 1974-08-07 | 1977-10-04 | Fluidrive Engineering Company Limited | Drives incorporating variable filling fluid couplings |
CH600191A5 (de) * | 1975-01-17 | 1978-06-15 | Voith Turbo Kg | |
DE2710927A1 (de) * | 1977-03-12 | 1978-09-14 | Daimler Benz Ag | Hydrodynamischer retarder fuer fahrzeuge, insbesondere fuer kraftfahrzeuge |
DE2918284C2 (de) * | 1979-05-07 | 1980-08-28 | Voith-Turbo Gmbh & Co Kg, 7180 Crailsheim | Pumpvorrichtung für eine Flüssigkeit |
DE3545660C1 (de) * | 1985-12-21 | 1987-06-25 | Voith Turbo Kg | Hydrodynamischer Stroemungskreislauf mit einer Einrichtung zur Reduktion der Luftventilationsleistung |
DE3743292A1 (de) * | 1987-12-19 | 1989-06-29 | Porsche Ag | Kupplung |
JP2816489B2 (ja) * | 1990-04-27 | 1998-10-27 | 曙ブレーキ工業株式会社 | リターダ制御装置 |
JPH061211A (ja) * | 1992-06-22 | 1994-01-11 | Akebono Brake Ind Co Ltd | 流体式リターダ制御装置 |
EP0707140B1 (de) * | 1994-10-12 | 1999-06-02 | Voith Turbo GmbH & Co. KG | Antriebseinheit mit einem Motor und einem Retarder |
DE19603148C1 (de) * | 1996-01-29 | 1997-07-03 | Voith Turbo Kg | Verfahren zur Kühlung des Betriebsmittels in Antriebseinheiten für Förderanlagen, insbesondere Kettenförderanlagen und Antriebseinheit |
DE19616426C1 (de) * | 1996-04-25 | 1997-08-14 | Voith Turbo Kg | Antriebseinheit mit einem Motor und einem Retarder |
DE19616425C1 (de) * | 1996-04-25 | 1997-07-24 | Voith Turbo Kg | Antriebseinheit mit einem Motor und einem Retarder |
-
1997
- 1997-02-22 DE DE19707172A patent/DE19707172C1/de not_active Expired - Fee Related
-
1998
- 1998-02-12 AU AU63978/98A patent/AU727786B2/en not_active Ceased
- 1998-02-12 GB GB9822133A patent/GB2328494B/en not_active Expired - Fee Related
- 1998-02-12 PL PL329375A patent/PL192535B1/pl unknown
- 1998-02-12 WO PCT/EP1998/000776 patent/WO1998037337A1/de active IP Right Grant
- 1998-02-12 US US09/171,665 patent/US6220024B1/en not_active Expired - Lifetime
- 1998-02-17 ZA ZA9801271A patent/ZA981271B/xx unknown
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE668327C (de) * | 1938-11-30 | J M Voith Maschinenfabrik | Turbogetriebe, insbesondere zum Antrieb von Kraftfahrzeugen | |
DE615344C (de) * | 1932-11-29 | 1935-07-04 | J M Voith Fa | Vorrichtung zum Betrieb hydraulischer Getriebe, die durch Fuellen eingerueckt und durch Entleeren ausgerueckt werden |
DE4224728A1 (de) | 1992-07-27 | 1994-02-10 | Voith Turbo Kg | Hydrodynamische Kupplung |
DE19512367A1 (de) | 1995-04-01 | 1996-10-02 | Voith Turbo Kg | Antriebseinheit für Förderanlagen, insbesondere Bandantriebsanlage |
Also Published As
Publication number | Publication date |
---|---|
AU727786B2 (en) | 2000-12-21 |
PL192535B1 (pl) | 2006-11-30 |
PL329375A1 (en) | 1999-03-29 |
AU6397898A (en) | 1998-09-09 |
US6220024B1 (en) | 2001-04-24 |
GB9822133D0 (en) | 1998-12-02 |
ZA981271B (en) | 1998-06-05 |
GB2328494A (en) | 1999-02-24 |
DE19707172C1 (de) | 1998-10-29 |
GB2328494B (en) | 2001-07-11 |
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