EP1971788A1 - Hydrodynamische kupplung - Google Patents
Hydrodynamische kupplungInfo
- Publication number
- EP1971788A1 EP1971788A1 EP07818353A EP07818353A EP1971788A1 EP 1971788 A1 EP1971788 A1 EP 1971788A1 EP 07818353 A EP07818353 A EP 07818353A EP 07818353 A EP07818353 A EP 07818353A EP 1971788 A1 EP1971788 A1 EP 1971788A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- wheel
- hydrodynamic coupling
- exhaust gas
- bladed
- primary
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn
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
- F16D33/02—Rotary fluid couplings or clutches of the hydrokinetic type controlled by changing the flow of the liquid in the working circuit, while maintaining a completely filled working circuit
- F16D33/04—Rotary fluid couplings or clutches of the hydrokinetic type controlled by changing the flow of the liquid in the working circuit, while maintaining a completely filled working circuit by altering the position of blades
Definitions
- the invention relates to a hydrodynamic coupling, that is a turbomachine, which operates on the Föttinger principle.
- Hydrodynamic couplings are known to have a bladed primary wheel, also called pump impeller, and a bladed secondary wheel, also called a turbine wheel. Both impellers face each other axially to form a separating gap and together form a generally toroidal working space.
- the working space can be filled with a working medium, for example oil, water or a mixture thereof, in order to transfer torque from the impeller to the turbine wheel via a working medium circuit in the working space which is established during operation of the hydrodynamic coupling.
- a particular application for a hydrodynamic coupling is a so-called turbocompound system.
- a turbocompound system which is generally used in a motor vehicle, for example a truck, a useful turbine is arranged in the exhaust gas stream of an internal combustion engine, which is acted upon by the exhaust gas.
- the power turbine converts the energy contained in the exhaust gas into a rotational movement.
- the rotational movement is transmitted to the crankshaft of the internal combustion engine to drive the crankshaft.
- a hydrodynamic coupling is introduced to the
- the hydrodynamic coupling in such a turbocompound system is designed as a constant filling coupling, that is, as a hydrodynamic coupling whose working space is always at least one predetermined Working fluid quantity is filled, the power turbine is protected from overspeeding due to lack of torque support.
- the impeller When applying a drive power to the shaft, the impeller moves on the external thread against the force of compression springs in the direction of the turbine wheel and thus "closes” the working fluid circuit in the working space, so that drive power from the impeller to the turbine wheel and thereby from the impeller bearing input shaft to a
- the force of the compression springs outweighs the force driving the pump impeller towards the turbine wheel from the input torque and drives the impeller away from the turbine wheel an interruption of the torque transmission from the impeller to the turbine reaches.
- hydrodynamic retarder are known in which the rotor with a return device, which a pressure surge on a rotor formed by the Piston surface selectively exerts, is axially displaceable from a working position to an idle position.
- a hydrodynamic retarder is described in German Utility Model DE 299 03 829 U1.
- patent specification DE 518 828 also describes a return device for the primary wheel or the secondary wheel of a hydrodynamic coupling, by means of which pressure oil can be selectively applied to a piston ring surface of the rotor of the displaceable wheel in order to effect an axial displacement.
- the present invention has for its object to provide a hydrodynamic coupling, in particular constant filling, in which the torque or rotational power transmission between the two paddle wheels is automatically high in a first direction and is interrupted or reduced in a second, opposite direction.
- the hydrodynamic coupling should have the simplest possible and compact construction and, in particular when used in a turbocompound system, improve this compared to the prior art.
- the hydrodynamic coupling according to the invention is particularly suitable for systems, for example turbocompound systems, in which certain Operating conditions, a torque transmission from the primary to the secondary takes place, and in other operating conditions, an undesirable torque transmission from the secondary to the primary wheel should be prevented or reduced, thus a kind of free-wheeling function should be achieved.
- At least one of the two wheels is mounted on a thread, in particular normal thread, coarse thread, swirl, helical or the like, that it by a rotational movement or a relative rotational movement relative to the thread / teeth in the axial direction of the hydrodynamic Clutch can be moved or moved so as to be approached in certain operating conditions in the direction of the other paddle or held with a predetermined minimum separation gap with respect to this, and can be traversed in other operating conditions of the other paddle wheel to the torque transmission through the working medium circuit largely or completely prevent or at least mitigate it.
- a helical toothing or the like may be provided, by means of which the movable bladed wheel is supported, usually on a shaft.
- the two bladed wheels can advantageously be mounted on a common shaft.
- one of the two bladed wheels for example the secondary wheel
- the second bladed wheel in particular the primary wheel
- the first bladed wheel thus rotates with the speed of the shaft, whereas the speed of the second bladed wheel rotates in accordance with the torque or rotational power transmission in the working space at a different speed.
- the hydrodynamic coupling advantageously has an oblique blading, that is to say the blades of the primary wheel and of the secondary wheel do not run in axial sectional planes through the axis of rotation, but are arranged at an angle thereto.
- the blades are not perpendicular to an axially perpendicular plane through the separation gap.
- the inclination or the angle of attack with respect to an axial section plane is such that the blades, which are advantageously aligned with each other, move in a first direction to each other in a first direction in a power transmission between the two paddles and in a second, opposite direction, moving spit each other.
- fleeing and Sp dirtyend are known in the art.
- Fled means that the inclination of the faster-rotating impeller, starting in the separating gap in the direction of the Schaufelrad Camills is designed in the direction of rotation
- spit means that the inclination of the Blades of the faster rotating paddle wheel, starting in the separating gap in the direction of the Schaufelradteils counter to the direction of rotation is executed.
- hydrodynamically relatively more power at the same amount of working fluid in the working space is transferred as in the fleeing operation.
- Exhaust gas energy utilization that is, with transmission of drive power from the exhaust gas turbine to the crankshaft, moves the movable paddle wheel automatically to the other paddle wheel or remains approached, because the primary wheel connected to the exhaust gas turbine rotates faster than the secondary wheel connected to the crankshaft.
- the startup and shutdown is thus exclusively due to the speed ratio between Primary and secondary determines or depending on which of the two wheels rotates faster compared to the other.
- the coupling according to the invention can be designed as a constant filling coupling.
- constant fill coupling in the present case is understood to mean a coupling in which the quantity of working medium in the working space and / or within the coupling varies, but there is always a minimum amount of working medium in the working space and / or the coupling.
- an external working medium circuit may or may not be provided.
- Figure 1 is a schematic diagram of a hydrodynamic coupling in one
- FIG. 2 shows a section through a hydrodynamic coupling designed according to the invention in a first operating state with a secondary wheel approached;
- Figure 3 shows the hydrodynamic coupling of Figure 2 in a second
- FIG. 4 shows a representation corresponding to FIG. 2 in a hydrodynamic coupling with inlet control
- Figure 5 shows the hydrodynamic coupling of Figure 4 in a worn state of the secondary wheel, in addition, a bypass is opened by the shutdown.
- FIG. 1 shows a turbocompound system with an internal combustion engine 10, which has a crankshaft 11, and an exhaust gas turbine 12 in the exhaust stream 13 of the internal combustion engine 10.
- the exhaust gas turbine 12 is in a drive connection with the crankshaft 11, in the present case via the gear train 15th , the hydrodynamic coupling 14 and the gear train 16.
- This drive connection if sufficient exhaust gas or exhaust gas energy is present in the exhaust stream 13, transmitted drive power from the exhaust gas turbine 12 to the crankshaft 11.
- the hydrodynamic coupling 14 is therefore provided to reduce or prevent this drag torque according to the invention with an axially displaceable paddle wheel, which automatically when the Abgaspiturbine 12 generates a drag torque is traversed by the other paddle wheel.
- FIGS. 2 to 5 A section through such a hydrodynamic coupling is shown in FIGS. 2 to 5.
- the primary wheel 1 is the secondary wheel 2, while maintaining a more or less large separation gap axially opposite.
- the size of the separating gap is determined by the axial position of the secondary wheel 2, which is directly supported on a thread 4 of a shaft 5.
- Both the primary wheel 1 and the secondary wheel 2 each have a blading 7, which is advantageously designed as an inclined blading.
- the shaft 5 carries a rolling bearing 6, here in the form of a double ball bearing, and the primary wheel. 1
- the working space 3 is always filled with a minimum amount of working fluid.
- the primary wheel 1 is connected via the flange 19 indirectly to the exhaust gas turbine (not shown).
- the secondary wheel 2 is (not shown) via the shaft 5 and a provided on this gear 20 or flange indirectly with the crankshaft (not shown).
- FIG 3 shows the conditions which result when the power flow from the crankshaft (not shown) via the secondary wheel 2 to the primary wheel 1 and then the exhaust gas utilization turbine (not shown) takes place, see the arrows.
- the secondary wheel 2 runs at a higher speed than the primary wheel 1.
- the secondary wheel 2 is thereby automatically driven off the primary wheel 1.
- the shutdown is again without the force of springs or a hydrodynamic actuator.
- the power transmission is prevented or at least reduced by the larger axial distance between the secondary 2 and the primary wheel 1.
- the inlet 8 is not closed, whereas it is closed in the extended state of the secondary wheel 2 ( Figure 5). This closing takes place automatically by the shutdown of the secondary wheel 2.
- the outlet opening of the inlet 8 is an inlet opening of a bore 9 in the secondary wheel 2 opposite.
- the bore 9 opens into the working space 3.
- the bore 9 is moved along, so that the inlet 8 in the extended state of the secondary wheel 2 of the bore 9 no longer faces. Rather, the inlet 8 is then closed by a radially inner surface of the secondary wheel 2.
- a bypass 21 may be provided, by means of which working medium in the worn state of the secondary wheel 2 is guided past the working space 3.
- this is achieved in that the bypass 21 facing the inlet 8 in the worn state of the secondary wheel 2 such that the working fluid is passed from the inlet 8 through the bypass 21 and outside the working chamber 3 and the coupling shell 18 is output.
- the bypass 21 is also executed in the case shown in the form of a bore through the secondary wheel 2.
- the mouth of the bypass 21 is axially offset from the inlet 8 and is covered by a radially outer surface of the shaft 5.
- the secondary wheel is shown as axially displaceable, additionally or alternatively, the primary wheel may be axially displaceable in order to achieve the effect according to the invention.
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE200610053175 DE102006053175A1 (de) | 2006-11-09 | 2006-11-09 | Hydrodynamische Kupplung |
PCT/EP2007/008265 WO2008055564A1 (de) | 2006-11-09 | 2007-09-22 | Hydrodynamische kupplung |
Publications (1)
Publication Number | Publication Date |
---|---|
EP1971788A1 true EP1971788A1 (de) | 2008-09-24 |
Family
ID=38820285
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP07818353A Withdrawn EP1971788A1 (de) | 2006-11-09 | 2007-09-22 | Hydrodynamische kupplung |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP1971788A1 (de) |
DE (1) | DE102006053175A1 (de) |
WO (1) | WO2008055564A1 (de) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102013113362B4 (de) * | 2013-12-03 | 2015-10-22 | Pierburg Gmbh | Regelbare Pumpe für eine Verbrennungskraftmaschine |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE518828C (de) * | 1928-11-06 | 1931-02-21 | Gustav Bauer Dr | Fluessigkeitsgetriebe |
US2359930A (en) | 1941-04-14 | 1944-10-10 | Hydraulic Brake Co | Fluid coupling |
DE8529980U1 (de) * | 1985-10-23 | 1986-02-06 | J.M. Voith Gmbh, 7920 Heidenheim | Hydrodynamische Bremse |
DE19522753C2 (de) * | 1995-06-26 | 1999-08-12 | Voith Turbo Kg | Anordnung einer hydrodynamischen Kupplung in einem Antriebssystem |
DE19835119C1 (de) * | 1998-08-04 | 2000-07-27 | Voith Turbo Kg | Hydrodynamische Maschine mit Brems- und Pumpfunktion |
DE29903829U1 (de) * | 1999-03-03 | 2000-07-20 | Voith Turbo Kg | Hydrodynamischer Retarder mit axial verschiebbarem Rotor und Rückstelleinrichtung |
JP4042582B2 (ja) * | 2003-02-07 | 2008-02-06 | いすゞ自動車株式会社 | 流体継手 |
DE10360055A1 (de) * | 2003-12-22 | 2005-07-21 | Voith Turbo Gmbh & Co. Kg | Hydrodynamische Kupplung |
DE102004002215B3 (de) * | 2004-01-15 | 2005-09-08 | Voith Turbo Gmbh & Co. Kg | Antriebskraftübertragungsvorrichtung mit hydrodynamischer Gegenlaufkupplung |
DE102005002108B4 (de) * | 2005-01-14 | 2008-02-07 | Voith Turbo Gmbh & Co. Kg | Hydrodynamische Strömungsmaschine mit axial verlagerbarem Schaufelrad |
-
2006
- 2006-11-09 DE DE200610053175 patent/DE102006053175A1/de not_active Withdrawn
-
2007
- 2007-09-22 EP EP07818353A patent/EP1971788A1/de not_active Withdrawn
- 2007-09-22 WO PCT/EP2007/008265 patent/WO2008055564A1/de active Application Filing
Non-Patent Citations (1)
Title |
---|
See references of WO2008055564A1 * |
Also Published As
Publication number | Publication date |
---|---|
WO2008055564A8 (de) | 2008-08-07 |
DE102006053175A1 (de) | 2008-05-15 |
WO2008055564A1 (de) | 2008-05-15 |
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Legal Events
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RAP1 | Party data changed (applicant data changed or rights of an application transferred) |
Owner name: VOITH PATENT GMBH |
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Effective date: 20090626 |
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Designated state(s): DE |
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STAA | Information on the status of an ep patent application or granted ep patent |
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18D | Application deemed to be withdrawn |
Effective date: 20110412 |