EP1313968A1 - Ensemble de demarrage - Google Patents

Ensemble de demarrage

Info

Publication number
EP1313968A1
EP1313968A1 EP01969394A EP01969394A EP1313968A1 EP 1313968 A1 EP1313968 A1 EP 1313968A1 EP 01969394 A EP01969394 A EP 01969394A EP 01969394 A EP01969394 A EP 01969394A EP 1313968 A1 EP1313968 A1 EP 1313968A1
Authority
EP
European Patent Office
Prior art keywords
clutch
starting unit
turbine wheel
wheel
clutch disc
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Withdrawn
Application number
EP01969394A
Other languages
German (de)
English (en)
Inventor
Heinz Höller
Reinhard Kernchen
Achim Menne
Werner Klement
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Voith Turbo GmbH and Co KG
Original Assignee
Voith Turbo GmbH and Co KG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority claimed from DE10110076A external-priority patent/DE10110076A1/de
Application filed by Voith Turbo GmbH and Co KG filed Critical Voith Turbo GmbH and Co KG
Publication of EP1313968A1 publication Critical patent/EP1313968A1/fr
Withdrawn legal-status Critical Current

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
    • F16D33/18—Details
    • 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
    • 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
    • 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
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0215—Details of oil circulation

Definitions

  • the invention relates to a starting unit, in particular with the features from the preamble of claim 1; furthermore a gear unit with a starting unit and a drive system with a starting unit designed according to the invention.
  • Starting units for use in manual transmissions, automated manual transmissions or automatic transmissions are known in a large number of designs. These include a hydrodynamic component in the form of a hydrodynamic speed / torque converter or a hydrodynamic clutch.
  • a hydrodynamic component in the form of a hydrodynamic speed / torque converter or a hydrodynamic clutch.
  • a possible design of a starting unit for use in transmissions with a hydrodynamic coupling reference is made to the publication DE 198 04 635 A1. This discloses an embodiment of a starting unit with a small axial length, comprising a pump wheel and a turbine wheel, which together form a toroidal working space, the pump wheel being arranged on the motor output side, ie the turbine wheel being arranged spatially between an input of the starting unit and the pump wheel.
  • the pump wheel is rotatably connected to the input or to a drive coupled to it via an element which simultaneously forms the pump wheel shell.
  • a lock-up clutch is provided, which is connected in parallel to the hydrodynamic clutch. This enables power transmission from the entrance of the start-up unit to the exit bypassing the hydrodynamic component.
  • the lock-up clutch is arranged as a separate component next to the pump wheel and turbine wheel unit.
  • the starting unit comprises a device for damping vibrations, which is arranged in a diameter range which is above the radially outer dimension of the toroidal working space Hydrodynamic clutch is arranged and is part of the lock-up clutch or forms a coupling element.
  • the device for damping vibrations is arranged essentially in the area of a plane or slightly offset from one another with the hydrodynamic coupling.
  • the invention is therefore based on the object of developing a starting unit of the type mentioned at the outset, comprising a hydrodynamic clutch and a lock-up clutch which are connected in parallel, in such a way that it is characterized by a small space requirement in the axial direction and a small number of components.
  • the design effort should be kept as low as possible.
  • the starting unit comprises an input that can be coupled to an drive and an output that can be coupled to an output.
  • a so-called impeller shell is assigned to the impeller, which is connected to it in a rotationally fixed manner and encloses the turbine impeller in the axial direction.
  • the pump wheel shell can be made in one piece with the pump wheel, but preferably multi-part designs are used, the non-rotatable connection being made via corresponding connecting elements or other coupling options.
  • the starting unit further comprises a switchable clutch in the form of a lock-up clutch, which is connected in parallel to the hydrodynamic clutch.
  • both clutches - hydrodynamic clutch and mechanical clutch - can also be jointly involved in the power transmission, ie both each transfer part of the total power.
  • the switchable clutch in particular a lock-up clutch, is designed as a mechanical clutch, preferably in a disk design.
  • This comprises at least a first clutch element in the form of a clutch input disk, also called a first clutch disk and a second clutch element in the form of a clutch output disk, also called a second clutch disk, which are connected to one another at least indirectly, ie either directly or indirectly via further transmission means, for example in the form of further disks, can be frictionally brought into operative connection.
  • an integration of components of the lock-up clutch in the hydrodynamic Component provided.
  • a clutch element usually a first clutch disc
  • the other second clutch disc is connected in a rotationally fixed manner to the turbine wheel.
  • the clutch disks are assigned means for generating a contact pressure and thus for generating an at least indirect frictional connection between the first clutch disk and the second clutch disk.
  • the solution according to the invention enables a starting unit to be designed with very little installation space in the axial direction, since here already existing components are simultaneously entrusted with the takeover of the function of the other element.
  • the means for generating a contact pressure comprise at least one piston element which can be pressurized with pressure medium. This can be assigned separately to the clutch discs. In a particularly compact and thus advantageous embodiment, however, the turbine wheel is used as a piston element.
  • the pressure chamber for acting on the piston element is formed by the part of the toroidal work chamber enclosed by the turbine wheel.
  • the indirect connection via further elements or direct frictional connection between the first clutch disc and the second clutch disc, which is non-rotatably connected to the turbine wheel is ensured by the displacement of the turbine wheel, while in the second case, only a reversible deformation of the connection between the turbine wheel and the outlet Starting unit that enables contact pressure.
  • the second solution is only suitable for designs with a small axial distance between the first and second clutch plates in the uncoupled state, while the first-mentioned solution is also conceivable for larger distances.
  • the turbine wheel can be axially displaced in a range of 0.1 to 2 mm.
  • a counterforce is required when the turbine wheel is axially displaceable, which fixes the position of the turbine wheel in relation to the pump impeller wheel.
  • this counterforce is generated by equipment supplied to the work space, which is guided along the outer circumference of the turbine wheel between the individual clutch disks of the lock-up clutch in the area of the parting plane between the pump wheel and turbine wheel in the area of the outer diameter of the toroidal work space and is introduced into the pump wheel from there , Usually both clutch disks are close to each other. The remaining gap serves as a throttle point for the equipment flowing through.
  • This throttle establishes a pressure difference between the piston surfaces which results in the required contact pressure for opening and closing for the bridging.
  • this can be implemented in designs with a rotationally fixed connection and axial displacement by pretensioning the turbine wheel, for example by means of at least one spring device.
  • this is also possible with the elastic connection of the turbine wheel to the outlet in the axial direction.
  • the equipment is now fed to the toroidal work area in the area of the inner circumference and flows through the hydrodynamic coupling centrifugally.
  • the pressure force generated by the operating medium on the turbine wheel causes the turbine wheel to be displaced or tilted in the direction away from the pump wheel, the clutch disk connected to the turbine wheel in a rotationally fixed manner being brought into operative connection with the clutch disk coupled to the pump wheel shell.
  • the spatial arrangement is viewed in the axial direction next to or behind the toroidal work space.
  • the arrangement in the radial direction is characterized by external and internal dimensions, which are preferably in the range between the outer and the inner diameter of the toroidal working space.
  • the friction surfaces which are formed by the clutch disks are preferably parallel to the parting plane between the pump wheel and aligned with the turbine wheel. Manufacturing tolerances can be compensated for without problems.
  • the rotationally fixed coupling to the turbine wheel is preferably carried out directly on the rear of the part of the turbine wheel which forms the toe.
  • the rotationally fixed connection of the individual clutch disks to the turbine wheel and the pump wheel or the pump wheel shell can also be realized in different ways. Are conceivable
  • the friction surface can be directly from the clutch disc, i.e. in the former case are formed by the outside of the turbine wheel and an inner surface of the pump wheel shell and in the second case by the separate component or by a friction lining assigned to the outer circumference of the turbine wheel or the individual clutch disks.
  • the design of the hydrodynamic coupling is a fluid coupling, that is, a component which, when transmitting power between an input and an output, only permits a speed change, ie is free of a change in the torque compared to a converter and is therefore necessarily coupled to the speed.
  • These can be regulated or unregulated.
  • regulated Hydrodynamic couplings are couplings in which the degree of filling can be changed during operation between full filling and emptying, whereby the power consumption and thus the transmission capacity of the coupling can be adjusted and, when used in vehicles, a stepless load-dependent speed control of the drive machine and / or output side is made possible.
  • the hydrodynamic clutch can be designed as a clutch with a toroidal working space, which is formed by a primary blade wheel functioning as a pump wheel and a secondary blade wheel functioning as a turbine wheel, or as a so-called double clutch, ie with two toroidal working spaces formed by the primary blade wheel and secondary blade wheel.
  • the controllability takes place primarily by changing the mass flow, ie influencing the degree of filling in the work area or the equipment circulation in the work cycle.
  • the control and / or regulation of the degree of filling of the hydrodynamic coupling is preferably carried out via a pressure control. Coupled with the change in the degree of filling is the change in the absolute pressure of the toroidal work space. Partial filling conditions can therefore be adjusted by changing the absolute pressure.
  • a particularly advantageous further development to ensure the sole as well as common power transmission via both clutches - hydrodynamic clutch and switchable clutch - and controllability of at least one power component that can be transmitted via one of the two clutches consists in one of each of the two operating material supply channels or rooms that can be used as inlet or outlet assign controllable valve device for controlling the pressure, with the power transmission via the hydrodynamic via the absolute pressure arising in the hydrodynamic clutch Clutch is controllable, while the power consumption of the switchable clutch can be adjusted via the differential pressure.
  • the starting unit comprises a device for damping vibrations, in particular a torsional vibration damper.
  • a device for damping vibrations is preferably arranged in series with the hydrodynamic component in the form of the hydrodynamic coupling and with the lock-up clutch.
  • the device for damping vibrations is arranged between the turbine wheel and the outlet.
  • the turbine wheel is coupled to the input of the device for damping vibrations or the input of the device for damping vibrations is connected in a rotationally fixed manner to the pump wheel via the pump wheel shell via the frictional connection when the hydrodynamic power branch is bridged.
  • the device for damping vibrations is viewed in the axial direction essentially in the area or in one plane with the hydrodynamic component.
  • the device for damping vibrations is arranged in the radial direction within the diameter describing the inner circumference of the part of the hydrodynamic coupling forming the toroidal working space. With this design, in addition to a particularly short axial length, the space available in the radial direction is optimally utilized. There are no restrictions with regard to the design of the device for damping vibrations, ie any type of vibration damper is conceivable. Devices for damping vibrations, which are based only on friction damping, or hydraulic damping devices are used, for example.
  • the design as a hydraulic damping device comprises in addition to a primary part and a secondary part, which are rotatably fixed to each other for the purpose of Torque transmission can be coupled, and can be rotated relative to one another in the circumferential direction by a certain angle, means for spring and / or damping coupling between the primary part and the secondary part.
  • the means for damping coupling comprise chambers which can be filled with hydraulic fluid and into which vibrations are displaced.
  • the device for damping vibrations only has to be designed for the output torque on the turbine wheel, which is why the device for damping vibrations in the radial and axial directions is very small and generally does not increase the dimensions of the starting unit predetermined by the hydrodynamic component.
  • connection options are also conceivable, for example the arrangement of the torsional vibration damper in series with the switchable clutch, i.e. before or after or before the power split.
  • the solution according to the invention is particularly suitable for use in automatic transmissions. These can be designed as manual transmissions or continuously variable transmissions.
  • the starting unit can be traded separately as a pre-assembled unit.
  • the connection to the transmission is made by integration in the transmission housing or series connection with switching stages or a continuously variable transmission part, e.g. traction mechanism transmission or toroidal transmission, whereby in both cases the coupling can be realized, for example, by plugging onto a shaft that can be coupled to the additional transmission stages or continuously variable transmission part.
  • the starting unit according to the invention is suitable for use in drive trains in stationary systems as well as vehicles.
  • FIGS. 1a and 1b illustrate an advantageous embodiment of a starting unit according to the invention
  • FIG. 2 illustrates a further development of a starting unit according to FIG. 1;
  • Figure 3 illustrates an advantageous embodiment of a
  • FIG. 5 shows a possibility of realizing a pressure control in a schematically highly simplified representation
  • FIG. 6 illustrates a simplification in terms of components according to
  • FIG. 1 a illustrates in a schematically simplified representation the basic structure of a starting unit 1 according to the invention. It comprises an input E that can be coupled with a drive and an output A that can be coupled with downstream transmission stages or an output.
  • the starting unit 1 comprises a starting element 2 in the form of a hydrodynamic coupling 3.
  • the hydrodynamic clutch 3 comprises two paddle wheels, a primary wheel functioning as a pump wheel 4 and a secondary wheel functioning as a turbine wheel 5, which together form a toroidal working space 6.
  • the starting unit 1 further comprises a lock-up clutch 7 connected in parallel to the start-up element 2 in the form of the hydrodynamic clutch 3.
  • a lock-up clutch is understood to be a switchable clutch device which enables power transmission in a drive system with several power branches bypassing one power branch.
  • the lock-up clutch 7 comprises at least two clutch elements which can be brought into a frictional connection, preferably in the form of clutch disks - viewed in the direction of force flow between the input E and the outlet A of the starting unit 1, a first clutch disk 8, which can also be referred to as a clutch input disk and a second clutch disk 9 , which is called the clutch output disc -.
  • An active connection by friction between the first Clutch disc 8 and the second clutch disc 9 can be realized directly or indirectly, in the former case the friction pairing is formed by the first clutch disc 8 and the second clutch disc 9, while in the second case further elements carrying friction surfaces are interposed.
  • the pump wheel 4 comprises a pump wheel shell 10.
  • the impeller shell 10 extends in the axial direction essentially over the axial extent of the turbine wheel 5 or at least partially encloses it in the radial direction.
  • the turbine wheel 5 is preferably enclosed by the pump wheel shell 10 or, in the case of a multi-part design, of its individual parts in such a way that they extend in the radial direction up to the area of the outlet A.
  • the turbine wheel 5 is connected directly or indirectly, ie via further transmission elements, to the output A of the starting unit 1.
  • the first clutch disc 8 is connected in a rotationally fixed manner to the pump wheel 4, in particular the pump wheel shell 10, while the second clutch disc 9 is coupled in a rotationally fixed manner to the turbine wheel 5.
  • the lock-up clutch 7 is preferably arranged in the radial direction in the region of the radial extension of the toroidal work space 6.
  • means 11 are also provided for generating a contact pressure for realizing a frictional connection between the two clutch plates, the clutch plate 8 and the second clutch plate 9.
  • the means 11 preferably comprise a piston element 12 to which pressure medium can be applied, the function of the piston element 12 being taken over by the turbine wheel 5 according to the invention.
  • the turbine wheel 5 is either non-rotatably connected to the output A, as indicated in the figure, but is designed to be displaceable in the axial direction, or the connection to the Output A is directly non-rotatable, torsionally rigid in the circumferential direction and elastic in the axial direction.
  • an embodiment with axial displaceability is preferred.
  • the operating medium is supplied to the working space 6 around the outer circumference 13 of the turbine wheel 5 and thus between the individual elements of the lock-up clutch 7, ie at least between the first clutch disc 8 and the second clutch disc 9.
  • the counterforce caused by the guidance when the operating medium flow is supplied enables the turbine wheel 5 to be axially fixed during power transmission in the hydrodynamic clutch 3.
  • This counterforce is eliminated by deflecting or changing the supply of the operating medium stream to the work area, the operating medium causes an axial force in the toroidal work area 6 due to the pressure building up in the work area 6, which is not supported by the turbine wheel 5, but rather to shift the turb inner wheel 5 leads in the axial direction.
  • This shift is on the order of 0.1 to 2 mm.
  • the displacement brings about a frictional connection between the two clutch plates, clutch plate 8 and second clutch plate 9, so that turbine wheel 5 is mechanically coupled to pump wheel 4, piston element 12, which is acted upon by a compressive force, being integrated in hydrodynamic clutch 3 is formed by the turbine wheel 5.
  • the part of the turbine wheel 5 carrying the second clutch disc 9 takes over the function of the piston element 12 and the operating medium located in the toroidal working chamber 6 takes over the function of pressurizing, in the case of a piston element 12 the function of the pressure chamber 14.
  • the embodiment of the starting unit 1 shown in FIG. 1 is a particularly advantageous arrangement of the individual elements - pump wheel 4 and turbine wheel 5 - of the hydrodynamic coupling 3.
  • the turbine wheel 5 In the transmission direction between the input E and the output A of the starting unit 1 the turbine wheel 5 is arranged spatially in the axial direction behind the pump wheel 4 or next to it, while the pump wheel 4 is arranged spatially between the input E and the turbine wheel 5.
  • the means 11 for generating a contact pressure for realizing a frictional connection of the individual elements of the lock-up clutch 7 in the hydrodynamic clutch 3 Due to the integration of the means 11 for generating a contact pressure for realizing a frictional connection of the individual elements of the lock-up clutch 7 in the hydrodynamic clutch 3, the number of components required can be reduced to a minimum, since no additional separate device for generating or providing the contact pressure for the individual elements, in particular the first clutch disk 8 and the second clutch disk 9 of the lock-up clutch 7 are required.
  • Another advantage is the short axial length due to the integrated design. In the case of optimized bucket wheels, this can be shortened even further with the solution according to the invention compared to the designs in the prior art.
  • the connection of the pump wheel 4 to the drive by means of fastening elements 15 takes place, the drive here not via the coupling of so-called flexplates 16 with a crankshaft 26 Drive machine 27 shown takes place, ie in the axial direction with flexible and torsionally rigid membranes.
  • the fastening elements 15 extend partially into the blade base 17 of the pump wheel 4. This is based on a detail from a constructive execution of a Starting unit 1 according to FIG. 1a is illustrated in FIG. 1b.
  • the second clutch disc 9 is preferably arranged on the rear side 18 of the turbine wheel.
  • the arrangement takes place parallel to the parting plane between the pump wheel 4 and the turbine wheel 5, preferably in the area between the dimensions of the inner diameter 19 and the outer diameter 20 of the toroidal work space 6.
  • the second clutch disc 9 is preferably formed directly by the turbine wheel 5, wherein the friction surface 21 is generated by a coating applied to the outer surface of the secondary wheel 5.
  • the starting unit 1.2 according to FIG. 2 comprises a device for damping vibrations 22, in particular a torsional vibration damper.
  • a device for damping vibrations 22 in particular a torsional vibration damper.
  • This can be designed in many forms, in the simplest case as a simple friction damper.
  • versions with hydraulic damping are also conceivable.
  • the specific design of a device for damping vibrations 22 reference can be made to those known from the prior art Explanations are referred. The specific selection is at the discretion of the responsible specialist.
  • the hydrodynamic component, the hydrodynamic clutch 3.2, the lock-up clutch 7.2 and the device 22 for damping vibrations are connected in series.
  • the device for damping vibrations 22 comprises a primary part 25, which is non-rotatably connected to the turbine wheel 5 and thus the second clutch disc 9 and a secondary part 23, which is non-rotatably coupled to the output. Means for damping and spring coupling 24 are provided between primary part 23 and secondary part 23.
  • the device for damping vibrations 22 is arranged depending on the power transmission branch in the power transmission via the hydrodynamic clutch 3.2 between the hydrodynamic clutch 3.2, in particular the turbine wheel 5.2 and the output A, furthermore in the case of power transmission via the lockup clutch 7.2 between the lockup clutch, in particular by the second clutch disc 9 formed output of the lock-up clutch and the output A of the starting unit.
  • the device 22 for damping vibrations is connected in series to the respective power-transmitting element - hydrodynamic clutch 3.2 or lock-up clutch 7.2.
  • the rest of the basic structure of the starting unit 1.2 corresponds to that described in FIG. 1a.
  • the same reference numerals are used for the same elements.
  • FIG. 3 illustrates in a schematically simplified representation a further embodiment of a starting unit 1.3 designed according to the invention with a starting element 2.3 in the form of a hydrodynamic coupling 3.3.
  • the hydrodynamic coupling 3.3 also comprises a primary wheel 4.3 and a secondary wheel 5.3, which together form a toroidal working space 6.
  • there is also one Bridging clutch 7 is provided, which is connected in parallel to the hydrodynamic clutch 3.3.
  • the basic function corresponds to that described in FIGS. 1 and 2.
  • the same reference numerals are used for the same elements.
  • the turbine wheel 5.3 is viewed spatially in the axial direction, arranged between the input E and the pump wheel 4.3, ie the pump wheel 4.3 is not on the motor side but on the motor side, contrary to the statements according to FIG. 1a and FIG Motor output side arranged.
  • the coupling between a drive, in particular the input E of the starting unit 1.3 and the pump wheel 4.3 takes place by enclosing the secondary wheel 5.3 in the axial direction, the connection of the turbine wheel 5.3 to the output via the output A in the radial direction within the space between the coupling between Input E and pump wheel 4.3 is arranged and viewed spatially between input E and output A of the starting unit before the coupling between input E and pump wheel 4.3.
  • Figures 1 to 3 illustrate advantageous configurations of starting units 1, 1.2 and 1.3 designed according to the invention. Further Functions can be implemented by additional modifications and are at the discretion of the responsible specialist.
  • FIGS. 4a and 4b illustrate the functioning of the starting unit 1.2 designed according to the invention using an embodiment according to FIG. 2; the same reference numerals are used for the same elements.
  • Figure 4a illustrates the supply of equipment to the work area 6.2 during hydrodynamic operation, i.e. Power transmission via the hydrodynamic clutch 3.2 around the outer circumference of the turbine wheel to the parting plane between the pump and turbine wheel 5.2 in the area of the outer diameter of the toroidal working space 6.2 and from there into the working space 6.2.
  • FIG. 1 illustrates the supply of equipment to the work area 6.2 during hydrodynamic operation, i.e. Power transmission via the hydrodynamic clutch 3.2 around the outer circumference of the turbine wheel to the parting plane between the pump and turbine wheel 5.2 in the area of the outer diameter of the toroidal working space 6.2 and from there into the working space 6.2.
  • 4b illustrates the changed operating medium guidance when switching over to the lockup clutch 7.2 to the turbine wheel 5.2 in the region of the inner circumference of the working space 6.2 for the purpose of building up pressure on the blade base of the turbine wheel 5.2 to the inner diameter of the toroidal working space.
  • FIG. 5 illustrates in a schematic simplified representation a preferred possibility of setting a partial filling of the hydrodynamic clutch 3.2 in a starting unit 1.2, as already described in FIGS. 1 to 3.
  • the degree of filling is changed by pressure control.
  • the equipment is guided outside the toroidal work space 6.2 for the purpose of cooling via an open circuit 29.
  • the change in the flow through the hydrodynamic coupling 3.2 takes place, for example, via a valve device 32, which determine the assignment of the individual equipment flow channels or lines to the inlet and outlet according to the switching position.
  • the inlet and outlet are designated 28 and 30, respectively, their coupling to the Resource management channels and rooms can be made as desired.
  • the connection shown at 28 acts as an inlet and the connection shown at 30 as a return.
  • the connection shown at 28 is coupled to channels (not shown in detail) for guiding the operating medium around the outer circumference of the turbine wheel.
  • the coupled flow of operating media when guided between the individual clutch disks 8 and 9 to be frictionally connected to one another, serves to deactivate the bridging coupling 7.2.
  • the hydrodynamic clutch is flowed through centripedally. This means a direction of flow towards the center, into the center of the working circuit 37 which arises in the toroidal working space.
  • the connection 30 serves to drain with operating materials from the toroidal working space 6.2.
  • the connection designated 28 functions as an outlet and the connection designated 30 as an inlet.
  • the operating medium is introduced centrifugally from the direction of the axis of rotation into the toroidal work space and effects the function shown in FIG.
  • the turbine wheel 5.2 of the hydrodynamic clutch 3.2 functions as a piston element for the clutch disks 8 and 9 of the lock-up clutch 7.2 which can be frictionally connected to one another.
  • the open circuit 29 is guided over a container 33. Coupled with this are a feed line 34 and a return line 35, which can optionally be coupled to the individual operating means guide channels or spaces via the valve device 32.
  • the feed line 34 is assigned to the connection 30, the return line 35 forms the connection 28.
  • a controllable pressure relief valve 36 is provided in the return line 35, which can limit the pressure in the return line 35 to a certain value.
  • a conveyor device 41 is also provided for the supply of operating resources. Another possibility according to FIG.
  • the inlet and outlet 30 or 28 from the toroidal work space are coupled to one another via a connecting line 37, which is coupled to an operating medium container 39 via a further connecting line 38.
  • the degree of filling in the toroidal working space 6.2 of the hydrodynamic coupling 3.2 can be controlled by changing the absolute pressure p ⁇ in the toroidal working space 6.2.
  • the connections 28 and 30 functioning as inlet and outlet are coupled to one another via the connecting line 37.
  • the individual connections 28 and 30 are each assigned controllable valve devices 40.1, 40.2 for controlling the pressures in the inlet and return - depending on the assignment of the individual connections 28 and 30 as a supply or drain line. In the simplest case, as shown in this figure, these are designed as independently controllable pressure control valve devices.
  • the connecting lines 37 and 38 as well as the connections 28 and 30 and the operating medium container 39 form an operating medium supply system 31.
  • a pressure relief valve 42 is provided in order to avoid delivery processes against the resistance of the valve devices 40.1 and 40.2.
  • first clutch disc second clutch disc 0 impeller shell 1 means for generating a contact pressure to realize a frictional connection - indirectly or directly - between the first clutch disc and the second clutch disc 2 piston element 3 outer circumference 4 pressure chamber 5 fastening elements 6 flexplate 7 blade base 8 rear 9 inner diameter 0 outer diameter 1 friction surface 2 device for damping vibrations 3 secondary part 4 means for damping and spring coupling 5 primary part 6 crankshaft 27 prime mover

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Friction Gearing (AREA)
  • Control Of Fluid Gearings (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)

Abstract

L'invention concerne un ensemble de démarrage (1) caractérisé en ce qu'il comprend une entrée (E) pouvant être accouplée à des moyens d'entrée et une sortie (A) pouvant être accouplée à des moyens de sortie ; un élément de démarrage (1) sous forme d'un accouplement hydrodynamique présentant une roue de pompe (4) et une roue de turbine (5) générant entre elles un espace de travail (6) de forme générale torique, une coque de roue de pompe (10) accouplée, solidaire en rotation, avec la roue de pompe (4) ; un accouplement de pontage (7) comprenant au moins deux disques d'accouplement pouvant être amenés par friction en liaison coopérante, directement ou indirectement, via d'autres moyens de transmission, à savoir, un premier disque (8) et un deuxième disque (9), le premier disque (8) étant connecté solidaire en rotation avec la coque de roue de pompe (10), et le deuxième disque (9) étant connecté solidaire en rotation avec la roue de turbine (5) ; ainsi que des moyens de production d'une force de pression en vue de réaliser une liaison par friction entre le premier disque d'accouplement (8) et le deuxième disque d'accouplement (9).
EP01969394A 2000-08-31 2001-07-16 Ensemble de demarrage Withdrawn EP1313968A1 (fr)

Applications Claiming Priority (7)

Application Number Priority Date Filing Date Title
DE10043146 2000-08-31
DE10043146 2000-08-31
DE10110076 2001-03-02
DE10110076A DE10110076A1 (de) 2000-08-31 2001-03-02 Anfahreinheit
EP01106407A EP1184598A1 (fr) 2000-08-31 2001-03-21 Unité de démarrage
DE1106407 2001-03-21
PCT/EP2001/008183 WO2002018818A1 (fr) 2000-08-31 2001-07-16 Ensemble de demarrage

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EP1313968A1 true EP1313968A1 (fr) 2003-05-28

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US (1) US20030168299A1 (fr)
EP (1) EP1313968A1 (fr)
JP (1) JP2004507691A (fr)
BR (1) BR0113526A (fr)
WO (1) WO2002018818A1 (fr)

Families Citing this family (29)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10251968A1 (de) * 2002-11-08 2004-05-19 Voith Turbo Gmbh & Co. Kg Hydrodynamische Kupplung und Anfahreinheit
DE10251971A1 (de) * 2002-11-08 2004-05-19 Voith Turbo Gmbh & Co. Kg Leistungsübertragungseinheit
DE10253838A1 (de) * 2002-11-18 2004-06-09 Voith Turbo Gmbh & Co. Kg Anfahreinheit und Getriebebaueinheit mit einer Anfahreinheit
DE102004029656A1 (de) * 2004-06-18 2006-01-19 Voith Turbo Gmbh & Co. Kg Hydrodynamische Kupplung mit Drehzahlschutz und Turbocompound-System
KR101311531B1 (ko) 2011-10-26 2013-09-25 한국파워트레인 주식회사 차량용 토크 컨버터
US9341261B2 (en) * 2014-07-14 2016-05-17 Gm Global Technology Operations, Llc Torque converter clutch control valve system
US9797494B2 (en) 2014-10-09 2017-10-24 Valeo Embrayages Hydrokinetic torque coupling device with turbine-piston lock-up clutch and epicyclic gearing
US9562597B2 (en) 2014-10-09 2017-02-07 Valeo Embrayages Hydrokinetic torque coupling device with turbine-piston lock-up clutch and bevel gearing
US9765872B2 (en) 2014-10-23 2017-09-19 Valeo Embrayages Hydrokinetic torque coupling device having turbine-piston lockup clutch with drive-clutch component, and related method
US9541181B2 (en) 2014-10-23 2017-01-10 Valeo Embrayages Torque converter and hydrokinetic torque coupling device having turbine-piston lockup clutch with flow restrictor, and related methods
US9441718B2 (en) 2014-10-23 2016-09-13 Valeo Embrayages Hydrokinetic torque coupling device having turbine-piston lockup clutch, and related methods
US9528586B2 (en) 2014-10-23 2016-12-27 Valeo Embrayages Hydrokinetic torque coupling device having turbine-piston lockup clutch and intermediate clutch component, and related methods
US9845854B2 (en) 2014-10-23 2017-12-19 Valeo Embrayages Hydrokinetic torque coupling device having turbine-piston lock-up clutch, and related methods
US9845855B2 (en) 2014-10-23 2017-12-19 Valeo Embrayages Torque converter and hydrokinetic torque coupling device having turbine-piston lockup clutch with lockup resistance member
US9297448B1 (en) 2014-10-23 2016-03-29 Valeo Embrayages Hydrokinetic torque coupling device having turbine-piston lockup clutch, and related methods
US9599206B2 (en) 2014-12-05 2017-03-21 Valeo Embrayages Torque converter and hydrokinetic torque coupling device having turbine-piston lockup clutch, and related methods
US9752667B2 (en) 2014-12-05 2017-09-05 Valeo Embrayages Torque converter and hydrokinetic torque coupling device having turbine-piston lockup clutch, and related methods
US9562598B2 (en) 2014-12-05 2017-02-07 Valeo Embrayages Torque converter and hydrokinetic torque coupling device having turbine-piston lockup clutch with lockup resistance member
US9574649B2 (en) 2014-12-05 2017-02-21 Valeo Embrayages Hydrokinetic torque coupling device having turbine-piston lockup clutch, and related methods
US9709145B2 (en) 2014-12-05 2017-07-18 Valeo Embrayages Torque converter and hydrokinetic torque coupling device having turbine-piston lockup clutch, and related methods
US9341250B1 (en) 2014-12-05 2016-05-17 Valeo Embrayges Hydrokinetic torque coupling device having turbine-piston lockup clutch, and related methods
US9523420B2 (en) 2014-12-05 2016-12-20 Valeo Embrayages Torque converter and hydrokinetic torque coupling device having core lockup clutch, and related methods
US9593755B2 (en) 2014-12-05 2017-03-14 Valeo Embrayages Hydrokinetic torque coupling device having turbine-piston lockup clutch, and related methods
US9739358B2 (en) 2015-04-15 2017-08-22 Valeo Embrayages Hydrokinetic torque coupling device having damper-piston lockup clutch, and related method
US10018260B2 (en) 2015-07-24 2018-07-10 Valeo Embrayages Hydrokinetic torque coupling device having turbine-piston lock-up clutch, and related methods
US10197143B2 (en) 2016-04-20 2019-02-05 Valeo Emrayages Hydrokinetic torque coupling device for motor vehicle
US10234007B2 (en) 2016-05-23 2019-03-19 Valeo Embrayages Hydrokinetic torque coupling device for motor vehicle
US10234008B2 (en) 2016-05-31 2019-03-19 Valeo Embrayages Hydrokinetic torque coupling device having axially movable turbine-piston and lockup clutch, and related methods
US10024411B2 (en) 2016-07-29 2018-07-17 Valeo Embrayages Hydrokinetic torque coupling device having turbine-piston lock-up clutch, and related methods

Family Cites Families (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2130895A (en) * 1936-12-24 1938-09-20 Deschimag Hydraulic coupling
US2731119A (en) * 1945-09-07 1956-01-17 Curtiss Wright Corp Hydraulic coupling construction
US2860747A (en) * 1953-04-09 1958-11-18 Gen Motors Corp Hydrodynamic drive devices
US3252352A (en) * 1963-02-18 1966-05-24 Ford Motor Co Hydrokinetic power transmitting mechanism
US3476219A (en) * 1968-03-22 1969-11-04 Eaton Yale & Towne Overmatching rotor to stator retarder arrangement to combat cavitation
US4317510A (en) * 1980-07-24 1982-03-02 General Motors Corporation Torque converter clutch having a viscous drive portion
JP2778033B2 (ja) * 1988-02-12 1998-07-23 トヨタ自動車株式会社 車両用フルードカップリング
WO1990005866A1 (fr) * 1988-11-17 1990-05-31 Zahnradfabrik Friedrichshafen Ag Procede de reglage d'un embrayage
US5078648A (en) * 1990-04-02 1992-01-07 Eaton Corporation Driveline isolator with hydraulic damper and spiral springs
US5771998A (en) * 1994-04-26 1998-06-30 Luk Lamellen Und Kupplungsbau Gmbh Force or torque transmitting apparatus with two hydraulic clutches
JP2956475B2 (ja) * 1994-05-25 1999-10-04 日産自動車株式会社 ロックアップ式無段変速装置
DE19626685A1 (de) * 1995-07-19 1997-01-23 Luk Getriebe Systeme Gmbh Hydrodynamischer Drehmomentwandler
JP3082131B2 (ja) * 1995-07-20 2000-08-28 本田技研工業株式会社 ロックアップクラッチの制御装置
US6016894A (en) * 1998-02-06 2000-01-25 Mannesmann Sachs Ag Hydrodynamic coupling device with a lockup clutch
DE19804635C2 (de) * 1998-02-06 2001-03-01 Mannesmann Sachs Ag Hydrodynamische Kupplungseinrichtung mit einer Überbrückungskupplung
DE19905625A1 (de) * 1998-02-17 1999-08-19 Luk Getriebe Systeme Gmbh Kraftübertragungseinrichtung
DE19909349A1 (de) * 1998-03-12 1999-09-16 Luk Getriebe Systeme Gmbh Hydrodynamischer Drehmomentwandler
JP2000266160A (ja) * 1999-03-12 2000-09-26 Isuzu Motors Ltd 流体伝動装置
BR0010378A (pt) * 1999-03-12 2001-12-26 Voith Turbo Kg Unidade de partida

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO0218818A1 *

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US20030168299A1 (en) 2003-09-11
WO2002018818A8 (fr) 2004-03-04
JP2004507691A (ja) 2004-03-11
BR0113526A (pt) 2003-07-08
WO2002018818A1 (fr) 2002-03-07

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